JP6915398B2 - Compressor - Google Patents

Description

The present invention relates to a scroll compressor.

Conventionally, a scroll compressor used in a gas injection cycle is known to have an injection port for injecting an intermediate pressure refrigerant into a compression chamber formed by a fixed scroll and a movable scroll.

The compressor described in Patent Document 1 is configured such that a compression chamber having a large confinement volume is formed on the radial outer side of the movable scroll, and a compression chamber having a small confinement volume is formed on the radial inside of the movable scroll. Asymmetric scroll compressor. The fixed scroll of this compressor is provided with injection ports at positions that alternately open to a compression chamber having a large confinement volume and a compression chamber having a small confinement volume as the movable scroll rotates. The injection port is provided at a position where it is opened for a longer time with respect to a compression chamber having a small confinement volume than a compression chamber having a large confinement volume. As a result, this compressor has a fixed scroll and a movable scroll by bringing the force acting on the movable scroll from the compression chamber having a large confinement volume and the force acting on the movable scroll from the compression chamber having a small confinement volume close to each other. It prevents the increase of the frictional force or the increase of the gap.

Japanese Patent No. 4265128

By the way, the compressor described in Patent Document 1 described above relates to a compressor having the same volume change rate of the compression chamber with respect to the rotation angle of the movable scroll, although the confined volumes of the two compression chambers are different.

On the other hand, the inventors have found a new problem regarding a compressor in which a plurality of compression chambers having different volume change rates are formed. That is, in such a compressor, the boosting speed of the refrigerant in the compression chamber having the larger volume change rate is faster than the boosting speed of the refrigerant in the compression chamber having the smaller volume change rate. The pressure difference between the two compression chambers is significantly larger than that of an asymmetric scroll compressor. When the rotation angle at which the two compression chambers are combined is reached in this state, the change in the compression reaction force when the pressure in each compression chamber is equalized becomes more rapid, which may cause a problem that torque fluctuation increases. There is.

Since the above-mentioned description of Patent Document 1 relates to a compressor having the same volume change rate of two compression chambers, it is necessary to solve a problem peculiar to a compressor having different volume change rates of a plurality of compression chambers. It is not a reference.

In view of the above points, it is an object of the present invention to reduce torque fluctuations of compressors having different volume change rates of a plurality of compression chambers.

In order to achieve the above object, the invention according to claim 1 is
A fixed plate (51) and a fixed scroll (50) having a spiral fixed wrap (52) provided on the fixed plate, and
A movable scroll (40) having a movable platen (41) and a spiral movable lap (42) provided on the movable platen, and revolving around a predetermined axis with the fixed lap and the movable lap fitted to each other. With and
In a scroll compressor in which a first compression chamber (61) and a second compression chamber (62) for compressing a refrigerant are formed between a fixed scroll and a movable scroll due to a decrease in volume due to the revolution of the movable scroll.
The volume change rate differs between the first compression chamber and the second compression chamber.
An injection port (11) is provided at a portion forming the first compression chamber having a small volume change rate.

According to this, the pressure difference between the first compression chamber and the second compression chamber caused by the revolution of the movable scroll is reduced by the injection of the refrigerant from the injection port. Therefore, when the first compression chamber and the second compression chamber are coupled at a predetermined rotation angle of the movable scroll, the torque fluctuation caused by the pressure equalization between the second compression chamber and the first compression chamber is reduced. Therefore, this compressor can reduce the noise vibration of the compressor due to the torque fluctuation and improve the controllability of the motor unit that revolves the movable scroll.

Further, the first compression chamber having a small volume change rate with respect to the rotation angle has a smaller step-up speed with respect to the rotation angle than the second compression chamber. Therefore, in the first compression chamber, the time from the start of compression until the refrigerant is boosted to the intermediate pressure (that is, the pressure of the refrigerant injected from the injection port) is longer than that in the second compression chamber. Therefore, since the time during which the refrigerant can be injected from the injection port becomes longer, the amount of the refrigerant that can be injected from the injection port increases. As a result, in the refrigeration cycle using this compressor, the heating or refrigerating capacity can be improved, and the coefficient of performance (COP) can be improved.

Further, by providing the injection port in the first compression chamber having a small rate of change in volume with respect to the rotation angle, the energy loss due to the re-expansion and recompression of the refrigerant can be reduced as compared with the case where the injection port is provided in the second compression chamber. Is possible. Therefore, this compressor can improve the compression efficiency of the compressor by reducing the influence of the dead volume due to the injection port.

The reference numerals in parentheses attached to each of the above configurations indicate an example of the correspondence with the specific configurations described in the embodiments described later.

It is a figure which showed the schematic structure of the refrigeration cycle using the compressor which concerns on 1st Embodiment on the Moriel diagram. It is sectional drawing including the shaft of a compressor. It is sectional drawing which shows a part of the fixed scroll and the movable scroll in the line III-III of FIG. It is explanatory drawing for demonstrating operation of a compressor. It is a graph which shows the relationship between the volume of a compression chamber and a rotation angle. It is a graph which shows the relationship between the pressure of a compression chamber and a rotation angle. It is a graph which shows the relationship between the pressure of a compression chamber and a rotation angle when injection is not performed. It is a graph which shows the relationship between a rotation angle and torque fluctuation. It is sectional drawing which shows a part of the fixed scroll and the movable scroll of the compressor of the comparative example. It is a graph which shows the relationship between the pressure of the 1st compression chamber of a comparative example, and a rotation angle. It is a graph which shows the relationship between the pressure of the 2nd compression chamber of a comparative example, and a rotation angle. It is sectional drawing which shows a part of the fixed scroll and the movable scroll of the compressor which concerns on 2nd Embodiment. It is sectional drawing which shows a part of the fixed scroll and the movable scroll of the compressor which concerns on 3rd Embodiment. It is sectional drawing which shows the 1st injection flow path of the compressor which concerns on 4th Embodiment. It is sectional drawing which shows the 2nd injection flow path of the compressor which concerns on 4th Embodiment. It is sectional drawing which shows the check valve provided in the 1st injection flow path of the compressor which concerns on 5th Embodiment. It is sectional drawing which shows the check valve provided in the 2nd injection flow path of the compressor which concerns on 5th Embodiment. It is sectional drawing which shows the check valve provided in the 1st injection flow path of the compressor which concerns on 6th Embodiment. It is sectional drawing which shows the check valve provided in the 1st injection flow path of the compressor which concerns on 6th Embodiment. It is sectional drawing which shows the check valve provided in the 2nd injection flow path of the compressor which concerns on 6th Embodiment. It is sectional drawing which shows the check valve provided in the 2nd injection flow path of the compressor which concerns on 6th Embodiment. It is a figure which showed the schematic structure of the refrigeration cycle using the compressor which concerns on 7th Embodiment on the Moriel diagram. It is a graph which shows the relationship between the pressure of the compression chamber of the compressor which concerns on 7th Embodiment, and the rotation angle. It is a graph which shows the relationship between the pressure of the 1st compression chamber of the compressor which concerns on 8th Embodiment, and the rotation angle. It is a graph which shows the relationship between the pressure of the 2nd compression chamber of the compressor which concerns on 8th Embodiment, and the rotation angle. It is a partial cross-sectional view of the compressor which concerns on 9th Embodiment. It is a graph which shows the relationship between the pressure of the compression chamber of the compressor which concerns on 9th Embodiment, and the rotation angle. It is sectional drawing which shows a part of the fixed scroll and the movable scroll of the compressor which concerns on 10th Embodiment. It is a graph which shows the relationship between the pressure of the compression chamber of the compressor which concerns on 10th Embodiment, and the rotation angle. It is sectional drawing which shows a part of the fixed scroll and the movable scroll of the compressor which concerns on 11th Embodiment.

Hereinafter, embodiments of the present invention will be described with reference to the drawings. In each of the following embodiments, parts that are the same or equal to each other will be described with the same reference numerals.

(First Embodiment)
The first embodiment will be described with reference to the drawings. As shown in FIG. 1, the compressor 1 of the present embodiment constitutes a part of the refrigeration cycle 100. The refrigeration cycle 100 is used for a hot water supply device, an air conditioner, or the like.

First, the configuration of the refrigeration cycle 100 including the compressor 1 of the present embodiment will be described. The refrigeration cycle 100 includes a compressor 1, a radiator 2, a first expansion valve 3, an intermediate heat exchanger 4, a second expansion valve 5, an evaporator 6, and the like. The refrigeration cycle 100 of the present embodiment is a gas injection cycle, in which a part of the high-pressure Ph refrigerant flowing out from the radiator 2 is branched, the pressure is reduced to the intermediate pressure Pm by the first expansion valve 3, and then the compressor 1 is used. A split circuit 9 for injecting is provided. The refrigerant that circulates in the refrigeration cycle 100 of the present embodiment is, for example, a fluid that mainly contains carbon dioxide.

The compressor 1 is a scroll type compressor 1 having an injection port 11. The compressor 1 has a configuration in which a refrigerant having an intermediate pressure of Pm is injected from the injection port 11 in the process of compressing the refrigerant sucked from the suction port 12. The compressor 1 mixes and compresses the refrigerant sucked from the suction port 12 and the refrigerant having an intermediate pressure Pm injected from the injection port 11, and discharges the refrigerant from the discharge port 13.

The high-pressure Ph refrigerant discharged from the discharge port 13 of the compressor 1 flows into the radiator 2. The radiator 2 exchanges heat between the inflowing refrigerant and water, air, or the like, which is a fluid to be heated (not shown), and dissipates heat from the refrigerant. The refrigerant flowing out of the radiator 2 is branched into two flows at the branch portion 7, one of the refrigerants flows to the high-pressure side heat exchange portion 4a of the intermediate heat exchanger 4, and the other refrigerant flows to the first expansion valve 3. Flow to.

The first expansion valve 3 is a decompressor that reduces the pressure of the refrigerant that has flowed in from the radiator 2. The first expansion valve 3 reduces the pressure of the refrigerant to an intermediate pressure Pm. The intermediate pressure Pm is the pressure between the high-pressure Ph refrigerant discharged from the discharge port 13 by the compressor 1 and the low-pressure Pl refrigerant sucked by the compressor 1 from the suction port 12. The refrigerant decompressed to the intermediate pressure Pm by the first expansion valve 3 flows to the intermediate pressure side heat exchange section 4b of the intermediate heat exchanger 4.

The intermediate heat exchanger 4 integrally includes a high-pressure side heat exchange unit 4a and an intermediate pressure side heat exchange unit 4b. As shown by the broken line arrow H1 in FIG. 1, the intermediate heat exchanger 4 flows into the intermediate pressure side heat exchange section 4b from the first expansion valve 3 and the refrigerant flowing into the high pressure side heat exchange section 4a from the radiator 2. Performs heat exchange with the refrigerant. The refrigerant flowing out from the intermediate pressure side heat exchange section 4b flows to the injection port 11 of the compressor 1 as shown by the arrow GI in FIG. On the other hand, the refrigerant flowing out from the high-pressure side heat exchange section 4a flows to the second expansion valve 5.

The second expansion valve 5 is a decompressor that reduces the pressure of the refrigerant that has flowed in from the high-pressure side heat exchange section 4a of the intermediate heat exchanger 4. The second expansion valve 5 decompresses the refrigerant to a pressure Pl lower than the intermediate pressure Pm. The refrigerant flowing out of the second expansion valve 5 flows to the evaporator 6.

The first expansion valve 3 of the present embodiment is an electrically driven expansion valve. The valve opening degree is adjusted by a control signal transmitted from the control device 8.

The refrigerant decompressed by the second expansion valve 5 flows into the evaporator 6. The evaporator 6 cools the fluid to be cooled by exchanging heat between the refrigerant and water or air which is a fluid to be cooled (not shown). The refrigerant absorbed from the fluid to be cooled while flowing through the flow path of the evaporator 6 is sucked from the evaporator 6 into the suction port 12 of the compressor 1.

Next, the configuration of the compressor 1 of the present embodiment will be described with reference to FIG. The compressor 1 includes a compression mechanism unit 10 for compressing the refrigerant, an electric motor unit 20 for driving the compression mechanism unit 10, a housing 30 for accommodating the compression mechanism unit 10 and the electric motor unit 20, and the like.

The housing 30 has a closed container structure in which a tubular member 31, an upper lid member 32 that closes one side of the tubular member 31, and a lower lid member 33 that closes the other side of the tubular member 31 are integrally joined. It has become.

The motor unit 20 has a stator 21 and a rotor 22 provided inside the stator 21. The stator 21 is composed of a stator core 23 and a stator coil 24 wound around the stator core 23.

A rotor 22 is fixed to the drive shaft 25, and a portion extending from the rotor 22 to the side opposite to the compression mechanism portion 10 is rotatably supported by a bearing 34 provided in the housing 30. A portion of the drive shaft 25 extending from the rotor 22 to the compression mechanism portion 10 side is rotatably supported by a bearing 36 provided in the middle housing 35.

An eccentric portion 26 is provided at a portion of the drive shaft 25 that extends further toward the compression mechanism portion 10 than the bearing 36. The eccentric portion 26 is formed in a columnar shape whose center position is deviated from the drive shaft 25, and is slidably fitted inside the fitting portion 49 of the movable scroll 40 constituting the compression mechanism portion 10. .. A balance weight 27 is provided on the opposite side of the eccentric portion 26 across the shaft of the drive shaft 25.

The compression mechanism unit 10 includes a movable scroll 40 and a fixed scroll 50. The fixed scroll 50 is fixed to the housing 30 or the middle housing 35. The movable scroll 40 is provided in a space formed between the middle housing 35 and the fixed scroll 50.

The fixed scroll 50 is formed with a suction port 12 (not shown in FIG. 2), a discharge port 13, an injection port 11, and a flow path communicating with those ports. The low-pressure refrigerant flowing out of the evaporator 6 is supplied to the suction flow path 14 communicating with the suction port 12.

The flow path communicating with the discharge port 13 forms a discharge space 15. A check valve 16 for discharge that allows the flow of refrigerant from the discharge port 13 to the discharge space 15 and regulates the flow of refrigerant from the discharge space 15 to the discharge port 13 between the discharge port 13 and the discharge space 15. Is provided. The refrigerant discharged from the discharge port 13 to the discharge space 15 flows to the radiator 2 via an oil separator (not shown).

The refrigerant of intermediate pressure Pm flowing out from the intermediate pressure side heat exchange section 4b of the intermediate heat exchanger 4 is supplied to the injection flow path 17 communicating with the injection port 11. The injection flow path 17 is provided with an injection check valve 18 that allows the flow of the refrigerant from the injection flow path 17 to the compression chamber side and regulates the flow of the refrigerant from the compression chamber to the intermediate pressure side heat exchange section 4b side. Has been done.

When electric power is supplied to the stator coil 24 from the terminal 38 provided in the housing 30, a rotating magnetic field is generated in the stator 21, and the rotor 22 and the drive shaft 25 are rotationally driven around the shaft. The rotational movement of the drive shaft 25 is transmitted from the eccentric portion 26 to the movable scroll 40 via the inner wall of the fitting portion 49. The movable scroll 40 is provided with a rotation prevention mechanism 48 for preventing rotation. Therefore, the movable scroll 40 revolves around the drive shaft 25 without rotating.

As shown in FIGS. 2 and 3, the fixed scroll 50 has a fixed plate 51 and a spiral fixed wrap 52 provided on the fixed plate 51. The movable scroll 40 has a movable platen 41 and a spiral movable lap 42 provided on the movable platen 41.

The fixed wrap 52 is provided so as to protrude from the fixed plate 51 toward the movable plate 41. The movable lap 42 is provided so as to protrude from the movable platen 41 toward the fixed platen 51. The fixed lap 52 and the movable lap 42 are installed in a state of being fitted to each other, and in this state, the movable scroll 40 revolves around the axis of the drive shaft 25.

Note that FIG. 3 illustrates only a part of the fixed scroll 50 and the movable scroll 40 of the compressor 1. It is assumed that the suction port 12 described above is provided at a portion of the fixed scroll 50 that is radially outside the fixed wrap 52 and the movable wrap 42. The discharge port 13 described above is provided at a portion of the fixed scroll 50 that forms a space 60 between the inner peripheral end of the fixed wrap 52 and the inner peripheral end of the movable wrap 42. And.

The movable scroll 40 and the fixed scroll 50 are in sliding contact with each other or adjacent to each other at a plurality of places. As a result, a compression chamber is formed between the movable scroll 40 and the fixed scroll 50. In the present embodiment, the compression chamber formed on the radial inside of the movable lap 42 of the movable scroll 40 is called the first compression chamber 61, and the compression chamber formed on the radial outside of the movable wrap 42 is called the second compression chamber. It will be called 62. The injection port 11 of the first embodiment is provided in the portion of the fixing plate 51 that forms the first compression chamber 61, and is not provided in the portion that forms the second compression chamber 62. That is, the injection port 11 of the first embodiment is provided in the portion of the fixing plate 51 that opens to the first compression chamber 61, and is not provided in the portion that opens to the second compression chamber 62. Therefore, in the first embodiment, the refrigerant having an intermediate pressure of Pm is injected from the injection port 11 into the first compression chamber 61 in the process of compressing the refrigerant in the first compression chamber 61.

Next, the operation of the compressor 1 will be described with reference to FIG. It should be noted that the specific numerical values of the rotation angles described in the following description are exemplified for the sake of easy understanding of the description, and do not limit the configuration and the scope of rights of the present embodiment. That is, the specific rotation angle in the operation of the compressor 1 can be appropriately changed depending on the number of turns or the profile of the fixed scroll 50 and the movable scroll 40 constituting the compressor 1.

FIG. 4 shows a state in which the movable scroll 40 revolves at every 45 ° of the rotation angle of the drive shaft 25 (hereinafter, may be simply referred to as “rotation angle”). FIG. 4A shows a state in which the outer peripheral end of the movable wrap 42 and the fixed wrap 52 are in contact or adjacent to each other, and the outer peripheral end of the fixed wrap 52 and the movable wrap 42 are in contact or adjacent to each other. Is shown. In this state, the closing of the first compression chamber 61 is completed inside the movable lap 42 in the radial direction, and the closing of the second compression chamber 62 is completed inside the movable lap 42 in the radial direction. When the movable scroll 40 revolves from this state, the first compression chamber 61 and the second compression chamber 62 move in the circumferential direction, and their volumes gradually decrease.

Further, in the state of (A) of FIG. 4, the injection port 11 has all or almost all of its opening area closed by the movable lap 42. When the movable scroll 40 revolves from this state, the injection port 11 starts to open in the first compression chamber 61.

As the state of (A) in FIG. 4 shifts to the states (B) to (F) of FIG. 4, the first compression chamber 61 and the second compression chamber 62 move in the circumferential direction, and their volumes are increased. Is getting smaller and smaller. In the compressor 1 of the present embodiment, in FIG. 4C, the end 43 on the inner peripheral side of the movable wrap 42 is slidably contacted or adjacent to the deep portion 53 of the fixed wrap 52, and thereafter, the second compression chamber is used. The structure is such that the movement of 62 inward in the circumferential direction is restricted. Therefore, between (C) of FIG. 4 and (F) of FIG. 4, the volume change rate of the second compression chamber 62 is larger than the volume change rate of the first compression chamber 61. As a result, the boosting speed of the refrigerant in the second compression chamber 62 becomes faster than the boosting speed of the refrigerant in the first compression chamber 61. After (F) of FIG. 4, when the first compression chamber 61 and the second compression chamber 62 are combined with the revolution of the movable scroll 40, as shown in FIG. 4 (G) and the like, the coupling compression chamber 63 Is formed.

In FIG. 4F, the injection port 11 is closed by the movable wrap 42 in almost all or all of its opening area.

Therefore, the injection port 11 has a rotation angle of 0 ° to 225 °. The injection port 11 may be provided at a position where the rotation angle is open even after 225 °. That is, the injection port 11 of the present embodiment starts to open in the first compression chamber 61 when the closing of the first compression chamber 61 is completed or immediately after that, and the first compression chamber 61 and the second compression chamber 62 are coupled. It is provided in an open position. The injection port 11 may be provided at a position where it is open even after the first compression chamber and the second compression chamber are combined.

The volume of the coupling compression chamber 63 in which the first compression chamber 61 and the second compression chamber 62 are coupled until the rotation angle further advances 360 ° from (F) of FIG. 4 and the state of (F) of FIG. 4 is reached again. Decreases. The refrigerant in the coupling compression chamber 63 is boosted by a decrease in the volume of the coupling compression chamber 63, and when the pressure of the refrigerant reaches the discharge pressure set in the compressor 1, the coupling compression chamber 63 of the fixed scroll 50 is formed. It is discharged from a discharge port 13 (not shown) provided at the site.

Subsequently, regarding the compressor 1 described above, the rotation angle of the drive shaft 25 and the change in the volume of the compression chamber will be described with reference to FIG.

The horizontal axis of FIG. 5 indicates the rotation angle, and the vertical axis indicates the volume of each compression chamber.

In FIG. 5, the change in the volume of the first compression chamber 61 is shown in the solid line V1, the change in the volume of the second compression chamber 62 is shown in the solid line V2, and the change in the volume of the coupling compression chamber 63 is shown in the solid line V3. The broken line V4 indicates the total volume of the first compression chamber 61 and the volume of the second compression chamber 62.

In FIG. 5, the description of the first compression chamber 61, the second compression chamber 62, and the coupling compression chamber 63 formed at a rotation angle of 360 ° or later, and the first compression formed at a rotation angle of 0 ° or earlier. The description of the chamber 61, the second compression chamber 62, and the coupling compression chamber 63 is omitted. This omission is the same for FIGS. 6, 7, 10, 11, 11, 23 to 25, 27, and 29, which will be described later.

The volume change rate of the first compression chamber 61 and the second compression chamber 62 is substantially the same from the rotation angle of 0 ° to the vicinity of 90 °. When the rotation angle exceeds around 90 °, the volume change rate of the second compression chamber 62 becomes larger than the volume change rate of the first compression chamber 61. When the rotation angle is around 225 °, the first compression chamber 61 and the second compression chamber 62 are coupled to form a coupling compression chamber 63. The volume of the coupling compression chamber 63 gradually decreases from around 225 ° to around 585 °.

Next, the rotation angle of the drive shaft 25 and the pressure change in the compression chamber will be described with reference to FIGS. 6 and 7. The horizontal axis of FIGS. 6 and 7 indicates the rotation angle, and the vertical axis indicates the pressure in each compression chamber (that is, the refrigerant pressure in the compression chamber). The horizontal axis and the vertical axis are the same for FIGS. 10, 11, 23, 25, and 27, which will be described later.

In FIG. 6, the pressure change of the first compression chamber 61 is shown by the solid line P1, the pressure change of the second compression chamber 62 is shown by the solid line P2, and the pressure change of the coupling compression chamber 63 is shown by the solid line P3. In FIG. 6, an example of the pressure (that is, the intermediate pressure Pm) of the refrigerant injected from the injection port 11 into the first compression chamber 61 is shown in Pm.

Further, in FIGS. 6 and 7, the pressure change of the first compression chamber 61 when the refrigerant of the intermediate pressure Pm is not injected from the injection port 11 into the first compression chamber 61 is shown by the broken line P4, and the coupling in that case. The pressure change in the compression chamber 63 is shown by the broken line P5.

Further, in FIG. 6, the range in which the injection port 11 is open to the first compression chamber 61 is indicated by a double-headed arrow Po. Further, the range in which the refrigerant is injected from the injection port 11 into the first compression chamber 61 is indicated by a double-headed arrow In.

As shown in FIG. 6, the refrigerant in the first compression chamber 61 is boosted by the decrease in the volume of the first compression chamber 61 due to the revolution of the movable scroll 40. Further, the refrigerant in the second compression chamber 62 is boosted by the decrease in the volume of the second compression chamber 62 due to the revolution of the movable scroll 40.

After the rotation angle of 0 °, the refrigerant having an intermediate pressure of Pm is injected into the first compression chamber 61 from the injection port 11 until the pressure of the first compression chamber 61 reaches the intermediate pressure Pm. Even after the intermediate pressure Pm is reached, the refrigerant in the first compression chamber 61 is boosted by a decrease in the volume of the first compression chamber 61. Then, when the first compression chamber 61 and the second compression chamber 62 are coupled at a rotation angle of about 225 °, the pressure of the first compression chamber 61 and the pressure of the second compression chamber 62 approximate. After that, the refrigerant in the coupling compression chamber 63 is boosted by the decrease in the volume of the coupling compression chamber 63 due to the revolution of the movable scroll 40. The refrigerant in the coupling compression chamber 63 is discharged from the discharge port 13 when the pressure reaches the discharge pressure of the compressor 1.

As shown in FIG. 5, since the volume change rate of the first compression chamber 61 is smaller than the volume change rate of the second compression chamber 62, the pressure increasing speed of the refrigerant in the first compression chamber 61 is that of the second compression chamber 62. It is slower than the pressurization speed of the refrigerant. Therefore, as shown by the broken line P4 and the solid line P2 in FIGS. 6 and 7, if the refrigerant having an intermediate pressure of Pm is not injected from the injection port 11 into the first compression chamber 61, the movable scroll 40 revolves and the first compression is performed. The pressure difference between the chamber 61 and the second compression chamber 62 becomes large. Then, when the first compression chamber 61 and the second compression chamber 62 are coupled at a rotation angle of about 225 °, the pressures of the two compression chambers 61 and 62 are equalized. At this time, there is a possibility that a problem such as an increase in torque fluctuation of the compressor 1 may occur.

Therefore, in the present embodiment, the injection port 11 is provided at a portion of the fixed plate 51 that forms the first compression chamber 61. Therefore, as shown in the solid lines P1 and P2 of FIG. 6, when the two compression chambers 61 and 62 are combined by the refrigerant injected into the first compression chamber 61 from the injection port 11, the two compression chambers 61 , 62 pressures approximate. Further, the opening area of the injection port 11 and the flow path resistance of the injection flow path 17 are also such that when the two compression chambers 61 and 62 are combined, the pressures of the two compression chambers 61 and 62 are approximated. It is set. Therefore, in the present embodiment, when the first compression chamber 61 and the second compression chamber 62 are combined, it is possible to suppress an increase in torque fluctuation of the compressor 1.

Subsequently, the relationship between the rotation angle of the drive shaft 25 and the torque fluctuation will be described with reference to FIG. The horizontal axis of FIG. 8 shows the rotation angle, and the vertical axis shows the torque fluctuation acting on the drive shaft 25 of the motor unit 20 that revolves the movable scroll 40.

In FIG. 8, if it is assumed that the refrigerant having an intermediate pressure Pm is not injected from the injection port 11 into the first compression chamber 61, the torque caused by the pressure in the first compression chamber 61 is shown by the broken line T1, and in that case, the second compression is performed. The torque caused by the pressure in the chamber 62 is shown by the broken line T2, and the torque caused by the pressure in the coupling compression chamber 63 in that case is shown by the broken line T3. Further, in that case, the torque fluctuation acting on the drive shaft 25 that revolves the movable scroll 40 is shown by the solid line T4. On the solid line T4, torque ripple is generated, and the torque fluctuation acting on the drive shaft 25 is large.

On the other hand, in the present embodiment, the refrigerant having an intermediate pressure of Pm is injected from the injection port 11 into the first compression chamber 61. The alternate long and short dash line T5 in FIG. 8 shows the torque fluctuation acting on the drive shaft 25 of the compressor 1 when the refrigerant having an intermediate pressure Pm is injected from the injection port 11 into the first compression chamber 61. As shown by the alternate long and short dash line T5, in the present embodiment, the torque fluctuation caused by the equalizing pressure between the second compression chamber 62 and the first compression chamber 61 is reduced.

Here, in order to compare with the compressor 1 of the present embodiment, the compressor 110 of the comparative example will be described with reference to FIGS. 9 to 11.

In the compressor 110 of the comparative example, two injection ports 111 and 112 are provided on the fixed plate 51 of the fixed scroll 50. The two injection ports 111 and 112 are provided in a portion of the fixing plate 51 that forms the first compression chamber 61 and a portion that forms the second compression chamber 62, respectively. In the following description, the injection port provided in the portion of the fixed plate 51 forming the first compression chamber 61 is referred to as the first injection port 111, and the injection port provided in the portion forming the second compression chamber 62 is the second injection port. It will be called the injection port 112.

In the comparative example, the opening area of the first injection port 111 and the opening area of the second injection port 112 are the same. Further, the flow path resistance of the first injection flow path communicating with the first injection port 111 and the flow path resistance of the second injection flow path communicating with the second injection port 112 are also the same. Therefore, the refrigerant pressure injected from the first injection port 111 into the first compression chamber 61 and the refrigerant pressure injected from the second injection port 112 into the second compression chamber 62 are the same.

FIG. 10 shows the relationship between the rotation angle of the drive shaft 25 and the pressure of the first compression chamber 61, and FIG. 11 shows the relationship between the rotation angle and the pressure of the second compression chamber 62.

In FIG. 10, the pressure change of the first compression chamber 61 when the injection is not performed is shown by the broken line P11, and the pressure change of the coupling compression chamber 63 at that time is shown by the broken line P12. Further, the pressure change of the first compression chamber 61 when injection is performed from the first injection port 111 is shown on the solid line P13, and the pressure change of the coupling compression chamber 63 at that time is shown on the solid line P14. The isentropic line is shown by the alternate long and short dash line E1.

Further, in FIG. 10, the range in which the first injection port 111 is open to the first compression chamber 61 is indicated by the double-headed arrow Po1. Further, the range in which the refrigerant is injected from the first injection port 111 into the first compression chamber 61 is indicated by the double-headed arrow In1.

In FIG. 11, the pressure change of the second compression chamber 62 when the injection is not performed is shown by the broken line P15, and the pressure change of the coupling compression chamber 63 at that time is shown by the broken line P16. Further, the pressure change of the second compression chamber 62 when the injection is performed from the second injection port 112 is shown by the solid line P17, and the pressure change of the coupling compression chamber 63 at that time is shown by the solid line P18. The isentropic line is shown on the alternate long and short dash line E2.

Further, in FIG. 11, the range in which the second injection port 112 is open to the second compression chamber 62 is indicated by the double-headed arrow Po2. Further, the range in which the refrigerant is injected from the second injection port 112 into the second compression chamber 62 is indicated by the double-headed arrow In2.

As shown in FIGS. 10 and 11, when injection is not performed, both the refrigerant in the first compression chamber 61 and the refrigerant in the second compression chamber 62 are theoretically compressed according to the isentropic lines E1 and E2. (Ie, adiabatic compression). The pressure of the first compression chamber 61 and the second compression chamber 62 is an intermediate pressure within the range in which the first injection port 111 and the second injection port 112 are opened in the first compression chamber 61 and the second compression chamber 62, respectively. A refrigerant having an intermediate pressure of Pm flows into each of the first compression chamber 61 and the second compression chamber 62 until the pressure does not exceed Pm. After that, the refrigerant in the first compression chamber 61 and the refrigerant in the second compression chamber 62 are compressed again according to the isentropic lines E1 and E2. Therefore, in the second compression chamber 62 having a large volume change rate, the step-up speed is high, so that the intermediate pressure Pm is reached early. As a result, as shown by the double-headed arrow In1 in FIG. 10 and the double-headed arrow In2 in FIG. 11, the injection range by the second injection port 112 provided in the second compression chamber 62 is the second one provided in the first compression chamber 61. 1 It is smaller than the injection range by the injection port 111.

Further, in the comparative example, the opening area and the flow path resistance of the first injection port 111 and the second injection port 112 are the same. Therefore, as the movable scroll 40 revolves, the pressure difference between the first compression chamber 61 and the second compression chamber 62 increases. Therefore, in the comparative example, when the first compression chamber 61 and the second compression chamber 62 are coupled at a rotation angle of about 225 °, the pressures of the two compression chambers 61 and 62 are equalized and the torque of the compressor 110 fluctuates. Will increase.

Compared to the compressor 110 of the comparative example described above, the compressor 1 of the present embodiment has the following effects.

(1) In the compressor 1 of the present embodiment, the injection port 11 is the first of the fixed plates 51 in a configuration in which the volume change rate of the first compression chamber 61 is smaller than the volume change rate of the second compression chamber 62. It is provided at a portion forming the compression chamber 61.

According to this, the pressure difference between the first compression chamber 61 and the second compression chamber 62 caused by the revolution of the movable scroll 40 is reduced by injecting the refrigerant from the injection port 11 into the first compression chamber 61. Therefore, when the first compression chamber 61 and the second compression chamber 62 are coupled at a predetermined rotation angle, the torque fluctuation caused by the pressure equalization between the second compression chamber 62 and the first compression chamber 61 is reduced. Therefore, the compressor 1 can reduce noise vibration due to torque fluctuations and improve the controllability of the motor unit 20 that rotates the drive shaft 25.

Further, the first compression chamber 61 having a small volume change rate with respect to the rotation angle has a smaller rate of increase in pressure with respect to the rotation angle than the second compression chamber 62. Therefore, the first compression chamber 61 takes longer than the second compression chamber 62 from the start of compression until the refrigerant is pressurized to the intermediate pressure (that is, the pressure of the refrigerant injected from the injection port 11). Therefore, since the time during which the refrigerant can be injected from the injection port 11 becomes longer, the amount of the refrigerant that can be injected from the injection port 11 increases. As a result, in the refrigerating cycle 100 using the compressor 1, the heating or refrigerating capacity can be improved, or the COP can be improved.

Further, by providing the injection port 11 in the first compression chamber 61 having a small rate of change in volume with respect to the rotation angle, energy loss due to re-expansion and recompression of the refrigerant is compared with the case where the injection port 11 is provided in the second compression chamber 62. Can be reduced. Therefore, the compressor 1 can improve the compression efficiency of the compressor by reducing the influence of the dead volume due to the injection port 11.

(2) In the present embodiment, the injection port 11 is a first compression chamber when the first compression chamber 61 and the second compression chamber 62 are combined by the refrigerant injected from the injection port 11 into the first compression chamber 61. The pressure difference between the 61 and the second compression chamber 62 can be reduced.

According to this, it is possible to reduce the torque fluctuation that occurs when the first compression chamber 61 and the second compression chamber 62 are coupled at a predetermined rotation angle.

(3) In the present embodiment, the injection port 11 is provided in the portion of the fixing plate 51 that forms the first compression chamber 61, not in the portion that forms the second compression chamber 62.

According to this, it is possible to reduce the dead volume of the compressor 1. Therefore, the compressor 1 can improve the compression efficiency of the compressor.

(4) In the present embodiment, the fixed scroll 50 and the movable scroll 40 are combined with the first compression chamber 61 and the second compression chamber 62 with the revolution of the movable scroll 40, and then further with the revolution of the movable scroll 40. After the refrigerant is compressed by reducing the volume of the coupling compression chamber 63, the refrigerant is discharged from the discharge port 13.

That is, the compressor 1 has a configuration in which the first compression chamber 61 compresses the refrigerant, the second compression chamber 62 compresses the refrigerant, and the coupling compression chamber 63 compresses the refrigerant at the same time.

(Second Embodiment)
The second embodiment will be described with reference to FIG. The second embodiment is a modification of the configuration of the injection port with respect to the first embodiment, and the other parts are the same as those of the first embodiment. Therefore, only the parts different from the first embodiment will be described.

In the compressor 1 of the second embodiment, the injection ports form a plurality of first injection ports 111 and a second compression chamber 62 provided at a portion of the fixed plate 51 that forms the first compression chamber 61. It is configured to include a second injection port 112 provided at the site. At least one of the first injection ports 111 is provided at a position where it starts to open in the first compression chamber 61 when or immediately after the closing of the first compression chamber 61 is completed. The second injection port 112 is also provided at a position where it starts to open in the second compression chamber 62 when the closing of the second compression chamber 62 is completed or immediately after that. Both the first injection port 111 and the second injection port 112 may be provided at positions that are open even after the first compression chamber and the second compression chamber are combined.

In the second embodiment, the number of the first injection ports 111 is larger than the number of the second injection ports 112. Thereby, the total opening area of the first injection port 111 can be made larger than the total opening area of the second injection port 112. Therefore, the amount of the refrigerant injected from the first injection port 111 into the first compression chamber 61 is larger than the amount of the refrigerant injected from the second injection port 112 into the second compression chamber 62. Therefore, in the second embodiment as well as in the first embodiment, it is possible to reduce the torque fluctuation that occurs when the first compression chamber 61 and the second compression chamber 62 are coupled at a predetermined rotation angle.

Further, in the second embodiment, the flow rate of the refrigerant supplied from the intermediate pressure to the compressor 1 can be increased by providing the first injection port 111 and the second injection port 112. Therefore, in the refrigerating cycle 100 using the compressor 1, the heating or refrigerating capacity can be improved, or the COP can be improved.

Further, in the second embodiment, the cross-sectional area of each injection port 11 can be reduced by increasing the number of injection ports 11. Therefore, the configuration of the second embodiment is suitable for the compressor 1 in which the thickness of the movable wrap 42 is thin.

In the second embodiment, the number of the first injection ports 111 may be larger than the number of the second injection ports 112, and the number of the first injection ports 111 and the number of the second injection ports 112 are shown in FIG. It is not limited to the number.

(Third Embodiment)
The third embodiment will be described with reference to FIG. The third embodiment is the same as the first and second embodiments in that the configuration of the injection port is changed with respect to the first and second embodiments, and therefore the first and second embodiments are the same. Only the parts that differ from the above will be described.

Also in the third embodiment, the injection ports are provided in the first injection port 111 provided in the portion of the fixed plate 51 forming the first compression chamber 61 and the second injection port provided in the portion forming the second compression chamber 62. It is configured to include an injection port 112. In the third embodiment, the opening area of the first injection port 111 is larger than the opening area of the second injection port 112. As a result, even in the third embodiment, the amount of refrigerant injected from the first injection port 111 into the first compression chamber 61 is larger than the amount of refrigerant injected from the second injection port 112 into the second compression chamber 62. Therefore, the third embodiment can also exhibit the same effects as those of the first and second embodiments.

In the third embodiment, the opening area of the first injection port 111 may be larger than the opening area of the second injection port 112, and the shapes of the first and second injection ports 111 and 112 are as shown in FIG. It is not limited to. In the third embodiment, the opening shape of the injection port 11 can be increased by forming a crescent shape that matches the shape of the movable wrap 42. With such a configuration, the third embodiment can also be adapted to the compressor 1 in which the thickness of the movable wrap 42 is thin.

(Fourth Embodiment)
A fourth embodiment will be described with reference to FIGS. 14 and 15. In the fourth embodiment, the configuration of the first injection flow path 171 communicating with the first injection port 111 and the configuration of the second injection flow path 172 communicating with the second injection port 112 are changed.

FIG. 14 shows the configuration of the first injection flow path 171 communicating with the first injection port 111. As shown by the alternate long and short dash arrow F1 in FIG. 14, the refrigerant injected from the first injection flow path 171 into the first compression chamber 61 via the first injection port 111 flows substantially linearly.

On the other hand, FIG. 15 shows the configuration of the second injection flow path 172 communicating with the second injection port 112. The second injection flow path 172 has a small diameter passage 172a, a medium diameter passage 172b, and a large diameter passage 172c. A tubular member 70 is fixed inside the large-diameter passage 172c. The tubular member 70 is in contact with a step 172d provided at a connection point between the medium-diameter passage 172b and the large-diameter passage 172c. The center position of the inner flow path 70a provided in the tubular member 70 and the small diameter passage 172a are deviated from each other. With this configuration, as shown by the alternate long and short dash arrow F2 in FIG. 14, the refrigerant injected from the second injection flow path 172 into the second compression chamber 62 via the second injection port 112 flows in a substantially crank shape. Therefore, the flow path resistance of the second injection flow path 172 is larger than the flow path resistance of the first injection flow path 171. Therefore, the flow rate of the refrigerant injected from the first injection flow path 171 into the first compression chamber 61 is larger than the flow rate of the refrigerant injected from the second injection flow path 172 into the second compression chamber 62.

In the fourth embodiment described above, similarly to the second and third embodiments, the amount of refrigerant injected from the first injection port 111 into the first compression chamber 61 is transferred from the second injection port 112 to the second compression chamber 62. It can be greater than the amount of refrigerant injected. Therefore, the fourth embodiment can also exhibit the same effects as those of the first to third embodiments.

(Fifth Embodiment)
A fifth embodiment will be described with reference to FIGS. 16 and 17. The fifth embodiment is also a modification of the configuration of the first injection flow path 171 communicating with the first injection port 111 and the configuration of the second injection flow path 172 communicating with the second injection port 112.

FIG. 16 shows the configuration of the first injection flow path 171 communicating with the first injection port 111. The first injection flow path 171 has a small diameter passage 171a, a medium diameter passage 171b, and a large diameter passage 171c. Inside the large-diameter passage 171c, a first reed valve 71 and a first tubular member 72 for fixing the first reed valve 71 are provided. The free end 71a of the first reed valve 71 is arranged on the small diameter passage 171a side. When the pressure of the refrigerant of the intermediate pressure Pm supplied to the first injection flow path 171 is higher than the pressure of the refrigerant of the first compression chamber 61, as shown by the broken line 71b in FIG. 16, the first lead valve 71 is free. The end 71a side is separated from the first tubular member 72. As a result, as shown by the alternate long and short dash arrow F3 in FIG. 16, the refrigerant injected from the first injection flow path 171 into the first compression chamber 61 via the first injection port 111 becomes a flow close to a straight line.

On the other hand, FIG. 17 shows the configuration of the second injection flow path 172 communicating with the second injection port 112. The second injection flow path 172 also has a small diameter passage 172a, a medium diameter passage 172b, and a large diameter passage 172c. Inside the large-diameter passage 172c, a second lead valve 73 and a second tubular member 74 for fixing the second lead valve 73 are provided. The free end 73a of the second lead valve 73 is arranged on the side opposite to the small diameter passage 172a. When the pressure of the refrigerant of intermediate pressure Pm supplied to the second injection flow path 172 is higher than the pressure of the refrigerant of the second compression chamber 62, as shown by the broken line 73b in FIG. 17, the second lead valve 73 is free. The end 73a side is separated from the first tubular member 72. As a result, as shown by the alternate long and short dash arrow F4 in FIG. 17, the refrigerant injected from the second injection flow path 172 into the second compression chamber 62 via the second injection port 112 is the free end of the second lead valve 73. It is a flow that largely bypasses 73a.

Therefore, the flow path resistance of the second injection flow path 172 is larger than the flow path resistance of the first injection flow path 171. Therefore, the flow rate of the refrigerant injected from the first injection flow path 171 into the first compression chamber 61 is larger than the flow rate of the refrigerant injected from the second injection flow path 172 into the second compression chamber 62.

In the fifth embodiment described above, similarly to the second to fourth embodiments, the amount of refrigerant injected from the first injection port 111 into the first compression chamber 61 is transferred from the second injection port 112 to the second compression chamber 62. It can be greater than the amount of refrigerant injected. Therefore, the fifth embodiment can also exhibit the same effects as those of the first to fourth embodiments.

(Sixth Embodiment)
The sixth embodiment will be described with reference to FIGS. 18 to 21. Also in the sixth embodiment, the configuration of the first injection flow path 171 communicating with the first injection port 111 and the configuration of the second injection flow path 172 communicating with the second injection port 112 are changed.

18 and 19 show the configuration of the first injection flow path 171 communicating with the first injection port 111. The first injection flow path 171 is provided with a first check valve 80. The first check valve 80 includes a case 81, a valve body 82, a stopper 83, and the like. The case 81 is formed in a tubular shape and is fixed to the inner wall of the first injection flow path 171. The valve body 82 is provided so as to be reciprocally movable inside the case 81. The stopper 83 is fixed to the inside of the case 81.

FIG. 18 shows the state of the first check valve 80 when the pressure of the first compression chamber 61 is lower than the intermediate pressure Pm. At this time, the valve body 82 is in contact with the tip portion 811 of the case 81. The refrigerant is injected from the intermediate heat exchanger 4 side into the first compression chamber 61 from the first injection port 111 through the gap 821 between the valve body 82 and the inner wall of the case 81 and the flow path 822 inside the valve body 82. Will be done.

FIG. 19 shows the state of the first check valve 80 when the pressure of the first compression chamber 61 is higher than the intermediate pressure Pm. At this time, the valve body 82 comes into contact with the stopper 83 and blocks the flow path inside the stopper 83. Therefore, the flow of the refrigerant from the first injection port 111 of the first compression chamber 61 to the intermediate heat exchanger 4 side is restricted.

20 and 21 show the configuration of the second injection flow path 172 communicating with the second injection port 112. A second check valve 85 is provided in the second injection flow path 172. The second check valve 85, like the first check valve 80, also includes a case 86, a valve body 87, a stopper 88, and the like. The case 86 is formed in a tubular shape and is fixed to the inner wall of the second injection flow path 172. The valve body 87 is provided so as to be reciprocally movable inside the case 86. The stopper 88 is fixed to the inside of the case 86.

FIG. 20 shows the state of the second check valve 85 when the pressure in the second compression chamber 62 is lower than the intermediate pressure Pm. At this time, the valve body 87 is in contact with the tip portion 861 of the case 86. The refrigerant is injected from the intermediate heat exchanger 4 side into the second compression chamber 62 from the second injection port 112 through the gap 871 between the valve body 87 and the inner wall of the case 86 and the flow path 872 inside the valve body 87. Will be done. However, the gap 871 between the valve body 87 included in the second check valve 85 and the inner wall of the case 86 is smaller than the gap 821 between the valve body 82 included in the first check valve 80 and the inner wall of the case 81. As a result, the flow path resistance of the second check valve 85 becomes larger than the flow path resistance of the first check valve 80. That is, the flow path resistance of the second injection flow path 172 is larger than the flow path resistance of the first injection flow path 171. Therefore, the flow rate of the refrigerant injected from the second injection flow path 172 into the second compression chamber 62 is smaller than the flow rate of the refrigerant injected from the first injection flow path 171 into the first compression chamber 61.

FIG. 21 shows the state of the second check valve 85 when the pressure in the second compression chamber 62 is higher than the intermediate pressure Pm. At this time, the valve body comes into contact with the stopper 88 and blocks the flow path inside the stopper 88. Therefore, the flow of the refrigerant from the second injection port 112 of the second compression chamber 62 to the intermediate heat exchanger 4 side is restricted.

In the sixth embodiment described above, similarly to the second to fifth embodiments, the amount of the refrigerant injected from the first injection port 111 into the first compression chamber 61 is transferred from the second injection port 112 to the second compression chamber 62. It can be greater than the amount of refrigerant injected. Therefore, the sixth embodiment can also exhibit the same effects as those of the first to fifth embodiments.

(7th Embodiment)
A seventh embodiment will be described with reference to FIGS. 22 and 23. The compressor 1 of the seventh embodiment also has a configuration including a first injection port 111 and a second injection port 112.

FIG. 22 shows the configuration of the refrigeration cycle 100 including the compressor 1 of the seventh embodiment. The refrigeration cycle 100 includes two branch portions 7a and 7b between the radiator 2 and the intermediate heat exchanger 4. The refrigerant branched at one of the branching portions 7a is depressurized to the first intermediate pressure Pm1 by the expansion valve 3a for the first injection flow path 171 to press the first intermediate pressure side heat exchange portion 4c of the intermediate heat exchanger 4. After passing through, it is injected into the first compression chamber 61 from the first injection port 111. The refrigerant branched at the other branch portion 7b is depressurized to the second intermediate pressure Pm2 by the expansion valve 3b for the second injection flow path 172, and the second intermediate pressure side heat exchange portion 4d of the intermediate heat exchanger 4 is depressurized. After passing through, it is injected into the second compression chamber 62 from the second injection port 112.

The intermediate heat exchanger 4 integrally includes a high-pressure side heat exchange unit 4a, a first intermediate pressure side heat exchange unit 4c, and a second intermediate pressure side heat exchange unit 4d. As shown by the dashed arrows H1 and H2 in FIG. 22, the intermediate heat exchanger 4 includes the refrigerant flowing through the high pressure side heat exchange section 4a, the refrigerant flowing through the first intermediate pressure side heat exchange section 4c, and the second intermediate pressure side heat. Heat exchange is performed with the refrigerant flowing through the switching unit 4d.

Both the expansion valve 3a for the first injection flow path 171 and the expansion valve 3b for the second injection flow path 172 are electrically driven expansion valves. The valve openings of the expansion valves 3a and 3b are adjusted by the control signal transmitted from the control device 8. Here, the first intermediate pressure Pm1 is set to a higher pressure than the second intermediate pressure Pm2. The first intermediate pressure Pm1 and the second intermediate pressure Pm2 are both a high-pressure Ph refrigerant discharged from the discharge port 13 by the compressor 1 and a low-pressure Pl refrigerant sucked from the suction port 12 by the compressor 1. Is the pressure between.

Next, the rotation angle and the pressure change in the compression chamber will be described with reference to FIG.

In FIG. 23, the pressure change of the first compression chamber 61 is shown by the solid line P19, the pressure change of the second compression chamber 62 is shown by the solid line P20, and the pressure change of the coupling compression chamber 63 is shown by the solid line P21. In FIG. 23, the pressure of the refrigerant injected from the first injection port 111 into the first compression chamber 61 (that is, the first intermediate pressure Pm1) is shown by a solid line Pm1. Further, the pressure of the refrigerant injected from the second injection port 112 into the second compression chamber 62 (that is, the second intermediate pressure Pm2) is shown by the solid line Pm2.

Further, in FIG. 23, the range in which the refrigerant is injected from the first injection port 111 into the first compression chamber 61 is indicated by the double-headed arrow In1. Further, the range in which the refrigerant is injected from the second injection port 112 into the second compression chamber 62 is indicated by the double-headed arrow In2.

In FIG. 23, the broken line P22 shows the pressure change of the first compression chamber 61 when the refrigerant of the first intermediate pressure Pm1 is not injected from the first injection port 111 into the first compression chamber 61. The broken line P23 shows the pressure change of the second compression chamber 62 when the refrigerant of the second intermediate pressure Pm2 is not injected from the second injection port 112 into the second compression chamber 62. The pressure change in the coupling compression chamber 63 in that case is shown by the broken line P24.

As shown in the solid line P19, in the first compression chamber 61, the first intermediate pressure from the first injection port 111 until the pressure of the first compression chamber 61 becomes the first intermediate pressure Pm1 after the rotation angle of 0 °. The Pm1 refrigerant is injected. Even after the first intermediate pressure Pm1 is reached, the refrigerant in the first compression chamber 61 is boosted by a decrease in the volume of the first compression chamber 61.

As shown by the solid line P20, the second compression chamber 62 has a second intermediate pressure from the second injection port 112 until the pressure of the second compression chamber 62 becomes the second intermediate pressure Pm2 after the rotation angle of 0 °. Pm2 refrigerant is injected. Even after the second intermediate pressure Pm2 is reached, the refrigerant in the second compression chamber 62 is boosted by a decrease in the volume of the second compression chamber 62.

Then, when the first compression chamber 61 and the second compression chamber 62 are combined, the pressure in the first compression chamber 61 and the pressure in the second compression chamber 62 approximate. After that, as shown by the solid line P21, the refrigerant in the coupling compression chamber 63 is boosted by the decrease in the volume of the coupling compression chamber 63 accompanying the revolution of the movable scroll 40. The refrigerant in the coupling compression chamber 63 is discharged from the discharge port 13 when the pressure reaches the discharge pressure of the compressor 1.

In the seventh embodiment, since the first intermediate pressure Pm1 is higher than the second intermediate pressure Pm2, the pressure in the first compression chamber 61 becomes the first after the compression of the refrigerant is started in the first compression chamber 61. The time until the pressure becomes higher than the intermediate pressure Pm1 becomes longer. Since the first intermediate pressure Pm1 is higher than the second intermediate pressure Pm2, the flow rate of the refrigerant injected from the first injection port 111 to the first compression chamber 61 side is increased from the second injection port 112 to the second compression chamber 62. It will be higher than the flow rate of the refrigerant injected to the side. Therefore, the amount of the refrigerant injected from the first injection port 111 into the first compression chamber 61 is larger than the amount of the refrigerant injected from the second injection port 112 into the second compression chamber 62. Therefore, the seventh embodiment can also exhibit the same effects as those of the first to fifth embodiments.

(8th Embodiment)
An eighth embodiment will be described with reference to FIGS. 24 and 25. In the eighth embodiment, the range in which the first and second injection ports 111 and 112 are opened and communicated with the first and second compression chambers 61 and 62, respectively, is changed with respect to the second to seventh embodiments. It is a thing.

FIG. 24 shows the relationship between the pressure and the rotation angle of the first compression chamber 61, and FIG. 25 shows the relationship between the pressure and the rotation angle of the second compression chamber 62.

In FIG. 24, the pressure change of the first compression chamber 61 when the injection is not performed is shown by the broken line P41, and the pressure change of the coupling compression chamber 63 at that time is shown by the broken line P42. Further, the pressure change of the first compression chamber 61 when injection is performed from the first injection port 111 is shown on the solid line P43, and the pressure change of the coupling compression chamber 63 at that time is shown on the solid line P44. The isentropic line is shown by the alternate long and short dash line E1.

Further, in FIG. 24, the range in which the first injection port 111 is open to the first compression chamber 61 is indicated by the double-headed arrow Po1. Further, the range in which the refrigerant is injected from the first injection port 111 into the first compression chamber 61 is indicated by the double-headed arrow In1.

In FIG. 25, the pressure change of the second compression chamber 62 when the injection is not performed is shown by the broken line P45, and the pressure change of the coupling compression chamber 63 at that time is shown by the broken line P46. Further, the pressure change of the second compression chamber 62 when the injection is performed from the second injection port 112 is shown by the solid line P47, and the pressure change of the coupling compression chamber 63 at that time is shown by the solid line P48. The isentropic line is shown on the alternate long and short dash line E2.

Further, in FIG. 25, the range in which the second injection port 112 is open to the second compression chamber 62 is indicated by the double-headed arrow Po2. Further, the range in which the refrigerant is injected from the second injection port 112 into the second compression chamber 62 is indicated by the double-headed arrow In2.

When injection is not performed, as shown in P41 and P45 of FIGS. 24 and 25, both the refrigerant in the first compression chamber 61 and the refrigerant in the second compression chamber 62 are theoretically issentropic lines E1 and E2. Compressed according to (ie, adiabatic compression).

When the injection is performed, as shown in P43 of FIG. 24, the first injection port 111 opens in the first compression chamber 61, and the pressure of the first compression chamber 61 does not exceed the intermediate pressure Pm in the range Po1. A refrigerant having an intermediate pressure of Pm flows into the first compression chamber 61. Further, as shown in P47 of FIG. 25, the second compression chamber is in the range Po2 in which the second injection port 112 is opened in the second compression chamber 62 and the pressure of the second compression chamber 62 does not exceed the intermediate pressure Pm. A refrigerant having an intermediate pressure of Pm flows into 62. Then again, the refrigerant in the second compression chamber 62 is compressed according to the isentropic line E2.

In the eighth embodiment, the first and second injection ports 111 and 112 are open and communicate with the first and second compression chambers 61 and 62, respectively, in the ranges Po1 and Po2, and since Po1 is longer, compression is performed. The range In1 in which the refrigerant can be injected within the range where the room pressure does not reach the intermediate pressure Pm is longer than that of In2. Therefore, the amount of the refrigerant injected from the first injection port 111 into the first compression chamber 61 is larger than the amount of the refrigerant injected from the second injection port 112 into the second compression chamber 62. Therefore, the eighth embodiment can also exhibit the same effects as those of the first to seventh embodiments.

(9th Embodiment)
A ninth embodiment will be described with reference to FIGS. 26 and 27. The ninth embodiment is a modification of the configuration of the second injection flow path 172 with respect to the second to eighth embodiments.

As shown in FIG. 26, in the ninth embodiment, the fixed plate 51 of the fixed scroll 50 is provided with a communication passage 90 that communicates the discharge space 15 that communicates with the discharge port 13 and the second injection port 112. .. A check valve 91 for a continuous passage is provided in the continuous passage 90. The check valve 91 for the continuous passage allows the flow of the refrigerant from the second injection port 112 side to the discharge space 15 side when the refrigerant pressure on the second injection port 112 side becomes higher than the refrigerant pressure in the discharge space 15. Has the function of Further, the check valve 91 for the continuous passage regulates the flow of the refrigerant from the discharge space 15 side to the second injection port 112 side when the refrigerant pressure on the second injection port 112 side is lower than the refrigerant pressure in the discharge space 15. It has a function.

A check valve 93 is also provided in the second injection flow path 172. The check valve 93 provided in the second injection flow path 172 is provided from the intermediate heat exchanger 4 side to the second injection port when the refrigerant pressure on the second injection port 112 side is lower than the refrigerant pressure on the intermediate heat exchanger 4 side. It has a function of allowing the flow of the refrigerant to the 112 side. Further, in this check valve 93, when the refrigerant pressure on the second injection port 112 side is higher than the refrigerant pressure on the intermediate heat exchanger 4 side, the flow of the refrigerant from the second injection port 112 side to the intermediate heat exchanger 4 side Has the function of regulating.

In FIG. 26, the first injection port 111 and the first injection flow path 171 are not shown.

In the configuration of the ninth embodiment, the rotation angle and the pressure change in the compression chamber will be described with reference to FIG. 27.

The pressure change in each compression chamber shown in FIG. 27 assumes a state in which the temperature and pressure of the refrigerant supplied from the evaporator 6 to the compressor 1 via the suction port 12 are relatively high.

In FIG. 27, the pressure change of the first compression chamber 61 is shown by the solid line P25, the pressure change of the second compression chamber 62 is shown by the solid line P26, and the pressure change of the coupling compression chamber 63 is shown by the solid line P27.

Further, in FIG. 27, the pressure change of the second compression chamber 62 when the communication passage 90 for communicating the discharge space 15 and the second injection port 112 and the check valve 91 for the communication passage is not provided is shown by the broken line P28. The pressure change of the coupling compression chamber 63 in that case is shown by the broken line P29.

As shown in FIG. 27, the refrigerant having an intermediate pressure Pm is injected into the second compression chamber 62 from the second injection port 112 until the pressure in the first compression chamber 61 reaches the intermediate pressure Pm after the rotation angle of 0 °. NS. Even after the intermediate pressure Pm is reached, the refrigerant in the second compression chamber 62 is boosted by a decrease in the volume of the second compression chamber 62. Therefore, as shown by the broken line P28, when the communication passage 90 and the check valve 91 for the communication passage that communicate the discharge space 15 and the second injection port 112 are not provided, the pressure of the second compression chamber 62 is the discharge pressure. The pressure exceeds. Therefore, when the first compression chamber 61 and the second compression chamber 62 are coupled, the torque fluctuation may become large due to the pressure equalization. In addition, there is a concern that the power loss of the motor unit 20 due to overcompression of the second compression chamber 62 will increase, and the compression efficiency of the refrigerant by the compressor 1 will decrease. Further, there is a possibility that the leakage loss of the refrigerant from the gap between the movable wrap 42 and the fixed plate 51 and the leakage loss of the refrigerant from the gap between the fixed wrap 52 and the movable plate 41 may increase.

On the other hand, in the ninth embodiment, when the refrigerant pressure in the second compression chamber 62 exceeds the discharge pressure when the second injection port 112 is open in the second compression chamber 62, the second compression chamber 62 It is possible to discharge the refrigerant from the second injection port 112 to the discharge space 15 via the communication passage 90 and the check valve 91 for the communication passage. Therefore, it is possible to reduce the torque fluctuation when the first compression chamber 61 and the second compression chamber 62 are coupled.

Further, in the ninth embodiment, it is possible to avoid the power loss of the compressor 1 due to overcompression in the second compression chamber 62 and prevent the compressor 1 from deteriorating the compression efficiency of the refrigerant. Further, it is possible to reduce the leakage loss of the refrigerant from the gap between the movable wrap 42 and the fixed plate 51 and the leakage loss of the refrigerant from the gap between the fixed wrap 52 and the movable plate 41.

Further, in the ninth embodiment, by using the second injection port 112 as a so-called relief port, the configuration is simplified, the dead volume is reduced, and the refrigerant is re-expanded, as compared with the case where the relief port is separately provided. , Energy loss due to recompression can be reduced.

(10th Embodiment)
The tenth embodiment will be described with reference to FIGS. 28 and 29. The tenth embodiment is the same as the first to eighth embodiments in which the relief port 19 is provided on the fixed scroll 50.

As shown in FIG. 28, in the tenth embodiment, the fixed plate 51 of the fixed scroll 50 is provided with the discharge port 13 and the relief port 19. The relief port 19 is provided at a portion of the fixing plate 51 that forms the second compression chamber 62. A check valve for relief (not shown) is provided in the flow path communicating with the relief port 19. The relief check valve has a function of allowing the refrigerant to flow from the relief port 19 to the relief flow path side (not shown) when the refrigerant pressure in the second compression chamber 62 exceeds a predetermined pressure, and from the relief flow path side. It has a function of regulating the flow of the refrigerant to the second compression chamber 62.

In the configuration of the tenth embodiment, the rotation angle and the pressure change in the compression chamber will be described with reference to FIG.

In FIG. 29, the pressure change of the first compression chamber 61 is shown by the solid line P31, the pressure change of the second compression chamber 62 is shown by the solid line P32, and the pressure change of the coupling compression chamber 63 is shown by the solid line P33.

Further, in FIG. 29, the pressure change of the first compression chamber 61 when the refrigerant of the intermediate pressure Pm is not injected from the injection port 11 into the first compression chamber 61 is shown by the broken line P34, and the coupling compression chamber 63 in that case is shown. The pressure change of is shown by the broken line P35. Further, in FIG. 29, the pressure change of the second compression chamber 62 when the relief port 19 is not provided in the second compression chamber 62 is shown by the broken line P36.

As shown by the broken line P36, when the relief port 19 is not provided in the second compression chamber 62, the pressure in the second compression chamber 62 may be higher than the pressure in the first compression chamber 61. In that case, when the first compression chamber 61 and the second compression chamber 62 are coupled, the torque fluctuation may become large due to the pressure equalization. In addition, there is a concern that the power loss of the motor unit 20 due to overcompression of the second compression chamber 62 will increase and the compressor efficiency will decrease. Further, there is a possibility that the leakage loss of the refrigerant from the gap between the movable wrap 42 and the fixed plate 51 and the leakage loss of the refrigerant from the gap between the fixed wrap 52 and the movable plate 41 may increase.

On the other hand, in the tenth embodiment, when the pressure in the second compression chamber 62 becomes higher than the predetermined pressure, the refrigerant in the second compression chamber 62 can be discharged from the relief port 19. Therefore, it is possible to reduce the torque fluctuation when the first compression chamber 61 and the second compression chamber 62 are coupled.

Further, in the tenth embodiment, it is possible to avoid a power loss of the compressor 1 due to overcompression in the second compression chamber 62 and prevent a decrease in compressor efficiency. Further, it is possible to reduce the leakage loss of the refrigerant from the gap between the movable wrap 42 and the fixed plate 51 and the leakage loss of the refrigerant from the gap between the fixed wrap 52 and the movable plate 41.

(11th Embodiment)
The eleventh embodiment will be described with reference to FIG. The compressor 1 of the eleventh embodiment is a multi-stage compressor in which a plurality of compression mechanisms are configured in the same end plate. The fixed lap 52 of the fixed scroll 50 and the movable lap 42 of the movable scroll 40 described in the first to tenth embodiments described above constitute the first stage compression mechanism 101.

In the compressor of the eleventh embodiment, the second stage compression mechanism 102 composed of the second fixed wrap 522 and the second movable wrap 422 is provided inside the first stage compression mechanism 101. In FIG. 30, for the sake of explanation, the boundary between the first-stage compression mechanism 101 and the second-stage compression mechanism 102 is indicated by the alternate long and short dash line 103.

The refrigerant sucked from the suction port 12 is compressed by the first-stage compression mechanism 101, and then flows into the compression chamber 602 of the second-stage compression mechanism 102 through a refrigerant flow path (not shown). Then, after being further compressed by the second-stage compression mechanism 102, it is discharged from a discharge port (not shown). Therefore, in the multi-stage compressor, the first-stage compression mechanism 101 is a low-stage side compressor, and the second-stage compression mechanism 102 is a high-stage side compressor.

By the way, the volume change rate of the compression chamber is determined by the lap shape. In a compressor that is continuously formed up to the center side like a conventional lap shape, the volume change rates of the compression chambers arranged inside and outside the movable scroll are equal. On the other hand, the compression mechanisms having different volume change rates of the compression chambers 61 and 62 arranged inside and outside the movable scroll as described in the first to tenth embodiments have an inflection point in the middle of the lap and perform multi-stage compression. It can be used as a low-stage compressor of the machine. Therefore, in the eleventh embodiment, by using the compression mechanism described in the first to tenth embodiments as the low-stage side compressor of the multi-stage compressor, the above-mentioned effects can be sufficiently exhibited.

(Other embodiments)
The present invention is not limited to the above-described embodiment, and can be appropriately modified within the scope of the claims. Further, the above-described embodiments are not unrelated to each other, and can be appropriately combined unless the combination is clearly impossible. Further, in each of the above embodiments, it goes without saying that the elements constituting the embodiment are not necessarily essential except when it is clearly stated that they are essential and when they are clearly considered to be essential in principle. stomach. Further, in each of the above embodiments, when numerical values such as the number, numerical values, amounts, and ranges of the constituent elements of the embodiment are mentioned, when it is clearly stated that they are particularly essential, and in principle, the number is clearly limited to a specific number. It is not limited to the specific number except when it is done. Further, in each of the above embodiments, when referring to the shape, positional relationship, etc. of a component or the like, the shape, unless otherwise specified or limited in principle to a specific shape, positional relationship, etc. It is not limited to the positional relationship.

(1) In each of the above embodiments, the first compression chamber 61 and the second compression chamber 62 complete the confinement of the refrigerant at the same rotation angle, and the first compression chamber 61 and the second compression chamber 62 compress the refrigerant. Although the configuration that proceeds at the same time has been described, the configuration of the compressor 1 is not limited to this. For example, in the compressor 1, the number of turns of the fixed wrap 52 is reduced, so that the rotation angle at which the refrigerant is closed by the first compression chamber 61 is larger than the rotation angle at which the refrigerant is closed by the second compression chamber 62. With a faster configuration, the pressure difference between the first compression chamber 61 and the second compression chamber 62 can be made smaller. Further, in any of the figures used in the explanation, the pressure in the compression chamber reaches the intermediate pressure Pm or the injection ports 111 and 112 are the compression chambers in the vicinity of the connection between the two compression chambers or at a rotation angle faster than that. The communication section is completed and the injection operation is completed, but the injection operation continues even after coupling depending on the pressure conditions (low pressure P1, intermediate pressure Pm), injection port specifications (position, opening area), and scroll wrap shape. This does not limit the effect, as it may occur.

(2) Further, in another embodiment, when the pressure difference between the first compression chamber 61 and the second compression chamber 62 becomes larger than a predetermined value, compression is performed from the split circuit 9 through the injection ports 11, 111, 112. The expansion valves 3, 3a, 3b and the like may be controlled so as to inject the refrigerant into the chamber.

(3) Further, in each of the above embodiments, the injection port has been described in the case where it is provided on the fixed plate, but it may be provided on the movable plate.

(summary)
According to the first aspect shown in part or all of the above embodiments, the fixed scroll has a fixed plate and a spiral fixed wrap provided on the fixed plate. The movable scroll has a movable platen and a spiral movable lap provided on the movable platen, and revolves around a predetermined axis in a state where the fixed lap and the movable lap are fitted to each other. A first compression chamber and a second compression chamber for compressing the refrigerant are formed between the fixed scroll and the movable scroll due to a decrease in volume due to the revolution of the movable scroll. The volume change rate is different between the first compression chamber and the second compression chamber. The compressor is provided with an injection port at a portion forming a first compression chamber having a small volume change rate.

According to the second aspect, the injection port is a first compression chamber and a second compression chamber when the first compression chamber and the second compression chamber are combined by the refrigerant injected into the first compression chamber from the injection port. It is configured to be able to reduce the pressure difference with.

According to this, it is possible to reduce the torque fluctuation that occurs when the first compression chamber and the second compression chamber are coupled at a predetermined rotation angle.

According to the third aspect, the compressor includes a first injection port provided at a portion forming the first compression chamber and a second injection port provided at a portion forming the second compression chamber. This compressor is configured so that the amount of refrigerant injected from the first injection port is larger than the amount of refrigerant injected from the second injection port.

According to this, it is possible to reduce the pressure difference between the first compression chamber and the second compression chamber caused by the revolution of the movable scroll. Therefore, it is possible to reduce the torque fluctuation that occurs when the first compression chamber and the second compression chamber are coupled at a predetermined rotation angle.

Further, by providing the first injection port and the second injection port on the fixed plate, the amount of refrigerant supplied from the intermediate pressure to the compressor can be increased.

According to the fourth viewpoint, the number of the first injection ports is larger than the number of the second injection ports.

According to this, the amount of the refrigerant injected into the first compression chamber from the intermediate pressure is made larger than the amount of the refrigerant injected into the second compression chamber, and the first compression chamber and the second compression generated by the revolution of the movable scroll The pressure difference in the chamber can be reduced. Therefore, it is possible to reduce the torque fluctuation that occurs when the first compression chamber and the second compression chamber are coupled at a predetermined rotation angle. Further, by providing the first injection port and the second injection port, the flow rate of the refrigerant supplied to the compressor can be increased.

By increasing the number of injection ports, the cross-sectional area of each injection port can be reduced, which is suitable for a compressor having a thin movable wrap.

According to the fifth aspect, the opening area of the first injection port is larger than the opening area of the second injection port.

According to this, the amount of the refrigerant injected into the first compression chamber from the intermediate pressure is made larger than the amount of the refrigerant injected into the second compression chamber, and the first compression chamber and the second compression generated by the revolution of the movable scroll The pressure difference in the chamber can be reduced. Therefore, it is possible to reduce the torque fluctuation that occurs when the first compression chamber and the second compression chamber are combined at a predetermined rotation angle of the movable scroll. Further, by providing the first injection port and the second injection port, the flow rate of the refrigerant supplied to the compressor can be increased.

It is also possible to increase the opening area of the injection port by making the opening shape of the injection port a crescent shape that matches the shape of the movable wrap.

According to the sixth aspect, the compressor further includes a first injection flow path communicating with the first injection port and a second injection flow path communicating with the second injection port. The compressor is configured so that the flow path resistance of the second injection flow path is larger than the flow path resistance of the first injection flow path.

According to this, the injection amount of the intermediate pressure refrigerant into the first compression chamber having a small volume change rate can be larger than the injection amount of the intermediate pressure refrigerant into the second compression chamber having a large volume change rate.

According to the seventh aspect, the compressor further includes a first injection flow path communicating with the first injection port and a second injection flow path communicating with the second injection port. The compressor is configured such that the pressure of the refrigerant injected from the first injection flow path into the first compression chamber is higher than the pressure of the refrigerant injected from the second injection flow path into the second compression chamber.

According to this, the flow rate of the refrigerant injected into the first compression chamber having a small volume change rate can be made larger than the flow rate of the refrigerant injected into the second compression chamber having a large volume change rate. Further, by increasing the pressure of the refrigerant injected into the first compression chamber from the first injection flow path, it is possible to prolong the time for injecting the refrigerant from the first injection port.

According to the eighth aspect, the range of the rotation angle at which the first injection port communicates with the compression chamber is configured to be wider than the range of the rotation angle at which the second injection port communicates with the compression chamber.

According to this, the amount of the refrigerant injected from the first injection port into the first compression chamber is larger than the amount of the refrigerant injected from the second injection port into the second compression chamber. Therefore, it is possible to reduce the torque fluctuation that occurs when the first compression chamber and the second compression chamber are coupled at a predetermined rotation angle.

According to the ninth aspect, the compressor further includes a discharge port, a discharge space, a continuous passage, and a check valve for the continuous passage. The discharge port is provided at a portion where the first compression chamber and the second compression chamber are combined to form a coupling compression chamber. The discharge space communicates with the discharge port. The communication passage communicates the second injection port with the discharge space. The check valve for the continuous passage is provided in the continuous passage to allow the flow of the refrigerant from the second injection port to the discharge space and regulate the flow of the refrigerant from the discharge space to the second injection port.

According to this, when the refrigerant pressure in the second compression chamber exceeds the discharge pressure when the second injection port is open in the second compression chamber, the refrigerant in the second compression chamber is discharged from the second injection port into the discharge space. It is possible to spit it out. Therefore, it is possible to avoid a power loss of the compressor due to overcompression in the second compression chamber and prevent a decrease in the compression efficiency of the refrigerant by the compressor. It is also possible to reduce the leakage loss of the refrigerant from the gap between the movable lap and the fixed plate and the leakage loss of the refrigerant from the gap between the fixed lap and the movable plate.

Furthermore, by using the second injection port as a so-called relief port, the configuration is simplified, the dead volume is reduced, and the energy loss due to the re-expansion and recompression of the refrigerant is reduced as compared with the case where the relief port is separately provided. It can be reduced.

According to the tenth aspect, the compressor further includes a relief port provided at a portion forming the second compression chamber.

According to this, when the refrigerant pressure in the second compression chamber, which has a large volume change rate before the first compression chamber and the second compression chamber are combined, exceeds a predetermined pressure, the refrigerant in the second compression chamber is relieved. It can be discharged from the port. Therefore, it is possible to reduce the torque fluctuation that occurs when the first compression chamber and the second compression chamber are combined. Further, it is possible to avoid power loss due to overcompression in the second compression chamber and prevent a decrease in the compression efficiency of the refrigerant by the compressor. It is also possible to reduce the leakage loss of the refrigerant from the gap between the movable lap and the fixed plate and the leakage loss of the refrigerant from the gap between the fixed lap and the movable plate.

According to the eleventh aspect, the injection port is not provided in the portion forming the second compression chamber, but is provided in the portion forming the first compression chamber.

According to this, it is possible to reduce the dead volume of the compressor. Therefore, this compressor can improve the compression efficiency of the refrigerant.

According to the twelfth viewpoint, in the fixed scroll and the movable scroll, the first compression chamber and the second compression chamber are combined to form a coupling compression chamber with the revolution of the movable scroll, and further, the coupling with the revolution of the movable scroll is formed. After the refrigerant is compressed by reducing the volume of the compression chamber, the refrigerant is discharged from the discharge port.

That is, this compressor has a configuration in which the first compression chamber compresses the refrigerant, the second compression chamber compresses the refrigerant, and the coupling compression chamber compresses the refrigerant as the movable scroll revolves.

According to the thirteenth viewpoint, the compressor is a multi-stage compressor composed of a plurality of compression mechanisms. That is, a second-stage compression mechanism composed of a second fixed wrap and a second movable wrap is provided inside the first-stage compression mechanism composed of the fixed lap and the movable wrap. Here, the first compression chamber and the second compression chamber having different volume change rates are configured in the first stage compression mechanism.

Here, the volume change rate is determined by the wrap shape. In a compressor that is continuously formed up to the center side like a conventional lap shape, the volume change rates of the compression chambers arranged inside and outside the movable scroll are equal. On the other hand, compression mechanisms having different volume change rates of compression chambers have an inflection point in the middle of lap, and can be used as a low-stage compressor of a multi-stage compressor. Therefore, the compression mechanisms having different volume change rates can fully exert their effects by using them as the low-stage compressor of the multi-stage compressor.

1 Compressor
11 Injection port 40 Movable scroll
41 Movable board
42 Movable wrap
50 fixed scroll
51 Fixed board
52 Fixed wrap
61 First compression chamber
62 Second compression chamber

Claims (13)

A fixed plate (51) and a fixed scroll (50) having a spiral fixed wrap (52) provided on the fixed plate, and a fixed scroll (50).
A movable scroll having a movable platen (41) and a spiral movable lap (42) provided on the movable platen, and revolving around a predetermined axis in a state where the fixed lap and the movable lap are fitted to each other. With (40)
In a scroll compressor in which a first compression chamber (61) and a second compression chamber (62) for compressing a refrigerant are formed between the fixed scroll and the movable scroll due to a decrease in volume due to the revolution of the movable scroll. ,
The first compression chamber and the second compression chamber have different volume change rates.
A compressor provided with an injection port (11) at a portion forming the first compression chamber having a small volume change rate. The injection port includes the first compression chamber and the second compression chamber immediately before the first compression chamber and the second compression chamber are combined with each other by the refrigerant injected from the injection port into the first compression chamber. The compressor according to claim 1, which is configured to be able to reduce the pressure difference between the two. A first injection port (111) provided at a portion forming the first compression chamber and a second injection port (112) provided at a portion forming the second compression chamber are provided.
The compressor according to claim 1 or 2, wherein the amount of refrigerant injected from the first injection port is configured to be larger than the amount of refrigerant injected from the second injection port. The compressor according to claim 3, wherein the number of the first injection ports is larger than the number of the second injection ports. The compressor according to claim 3 or 4, wherein the opening area of the first injection port is larger than the opening area of the second injection port. The first injection flow path (171) communicating with the first injection port and
A second injection flow path (172) communicating with the second injection port is further provided.
The compressor according to any one of claims 3 to 5, wherein the flow path resistance of the second injection flow path is configured to be larger than the flow path resistance of the first injection flow path. A first injection flow path communicating with the first injection port,
A second injection flow path communicating with the second injection port is further provided.
The pressure of the refrigerant injected into the first compression chamber from the first injection flow path is configured to be higher than the pressure of the refrigerant injected into the second compression chamber from the second injection flow path. The compressor according to any one of claims 3 to 6. The range of the rotation angle at which the first injection port communicates with the first compression chamber is
The compressor according to any one of claims 3 to 7, wherein the second injection port is configured to be wider than a range of rotation angles communicating with the second compression chamber. A discharge port (13) provided at a portion forming a coupling compression chamber (63) in which the first compression chamber and the second compression chamber are combined.
A discharge space (15) communicating with the discharge port and
A communication passage (90) communicating the second injection port and the discharge space,
A check valve for a continuous passage (91) provided in the continuous passage, which allows the flow of the refrigerant from the second injection port to the discharge space and regulates the flow of the refrigerant from the discharge space to the second injection port. ), The compressor according to any one of claims 3 to 8. The compressor according to any one of claims 1 to 9, further comprising a relief port (19) provided at a portion forming the second compression chamber. The compressor according to claim 1 or 2, wherein the injection port is not provided at a portion forming the second compression chamber, but is provided at a portion forming the first compression chamber. In the fixed scroll and the movable scroll, the first compression chamber and the second compression chamber are combined to form a coupling compression chamber as the movable scroll revolves, and further, the coupling compression accompanying the revolution of the movable scroll. The compressor according to any one of claims 1 to 11, wherein the refrigerant is discharged from the discharge port after the refrigerant is compressed by reducing the volume of the chamber. The compressor is a multi-stage compressor composed of a plurality of compression mechanisms.
A second-stage compression mechanism (422) composed of a second fixed wrap (522) and a second movable wrap (422) is inside the first-stage compression mechanism (101) composed of the fixed wrap and the movable wrap. 102) is provided,
The compressor according to any one of claims 1 to 12, wherein the first compression chamber and the second compression chamber having different volume change rates are configured in the first stage compression mechanism.

Images