JP7745664B2 - Compressor and refrigeration cycle device equipped with said compressor - Google Patents

Description

This disclosure relates to a compressor and a refrigeration cycle device equipped with the compressor.

Conventionally, compressors such as those disclosed in Patent Document 1 are known that include a sealed container, an electric motor, a rotating shaft, and a compression mechanism. The compression mechanism includes a cylinder having a cylinder chamber, a rolling piston that is fitted onto the eccentric shaft of the rotating shaft and housed in the cylinder chamber, rotating together with the eccentric shaft to compress the refrigerant, and a vane that is located in a vane groove formed radially in the cylinder and follows the rolling piston to separate the cylinder chamber into a refrigerant suction chamber and a compression chamber.

In recent years, as one of the measures to combat global warming, low GWP (Global Warming Potential) refrigerants, such as R32, R1234yf, or R290, have been used as refrigerants in refrigeration cycle systems equipped with compressors. However, low GWP refrigerants have lower refrigeration capacity per volume compared to traditional refrigerants such as R410A. For this reason, in refrigeration cycle systems, the flow rate of refrigerant flowing through the system must be increased to achieve the desired refrigeration capacity. Increasing the stroke volume of the compression chamber is an effective way to increase the refrigerant flow rate. Stroke volume is the amount of refrigerant discharged per rotation by the compression mechanism. To increase this stroke volume, it is desirable to enlarge the inner diameter of the cylinder chamber.

WO 2018/87955

However, in conventional compressors such as that disclosed in Patent Document 1, increasing the inner diameter of the cylinder chamber increases the amount by which the vanes protrude into the cylinder chamber. If the vanes protrude too far into the cylinder chamber relative to their overall length, their operation becomes unstable and their ability to follow the rolling piston deteriorates. As a result, the compressor may experience refrigerant leakage from the high-pressure chamber to the low-pressure chamber in the cylinder chamber, reducing compression efficiency. Furthermore, because the lateral area of the vanes that support the load of the refrigerant differential pressure acting from the high-pressure chamber to the low-pressure chamber is reduced, harsh sliding conditions occur, causing the vanes to seize and resulting in compressor failure.

The present disclosure has been made to solve the above-mentioned problems, and aims to provide a compressor and a refrigeration cycle device equipped with the compressor that can suppress refrigerant leakage and seizure from the high-pressure chamber to the low-pressure chamber even if the inner diameter of the cylinder chamber of the cylinder is enlarged and the amount of protrusion of the vane into the cylinder chamber increases.

A compressor according to the present disclosure includes a sealed container forming an outer shell, an electric motor unit having a stator and a rotor, a rotating shaft connected to the rotor and transmitting a driving force of the electric motor unit, and a compression mechanism unit connected to the rotating shaft and compressing a refrigerant by the driving force transmitted from the rotating shaft, wherein the rotating shaft has an eccentric shaft portion, and the compression mechanism unit includes: a cylinder fixed to the sealed container and having a cylinder chamber into which a refrigerant is drawn and compressed; a rolling piston fitted to the eccentric shaft portion and housed in the cylinder chamber, and rotating together with the eccentric shaft portion to compress the refrigerant; and a vane provided in a vane groove formed in a radial direction of the cylinder, and following the rolling piston to divide the cylinder chamber into a refrigerant suction chamber and a compression chamber ; A recess in which the vane can slide is formed on the inner wall surface of the vessel, and the vane groove does not penetrate all the way to the outer peripheral surface of the cylinder at one of the two opposing end surfaces of the cylinder, but has a stop portion for the vane at an end on the outer peripheral surface side of the cylinder, and is formed at the other end surface side of the cylinder so as to penetrate the outer peripheral surface of the cylinder, and the length of the vane along the radial direction of the portion located on the one end surface side of the cylinder is longer than the length along the radial direction of the portion located on the other end surface side of the cylinder, and when the rolling piston is positioned in a phase of top dead center, the portion located on the other end surface side of the cylinder protrudes from the outer peripheral surface of the cylinder into the recess .

The refrigeration cycle device of the present disclosure has a refrigeration circuit in which at least the above-mentioned compressor, an outdoor heat exchanger that exchanges heat between the refrigerant flowing inside and the outdoor air, an indoor heat exchanger that exchanges heat between the refrigerant flowing inside and the indoor air, and an expansion mechanism that expands the refrigerant flowing into the outdoor heat exchanger or the indoor heat exchanger are connected via refrigerant piping.

According to the present disclosure, the radial length of the vane at the portion located on the other end face of the cylinder that penetrates the outer peripheral surface is longer than the radial length of the portion located on one end face of the cylinder where the stop portion is formed. Therefore, the amount of protrusion of the vane into the cylinder chamber relative to its overall length can be reduced, and the side area of the vane can be increased. Therefore, even if the inner diameter of the cylinder chamber of the cylinder is enlarged and the amount of protrusion of the vane is increased, refrigerant leakage from the high-pressure chamber to the low-pressure chamber and seizure can be suppressed.

1 is a longitudinal sectional view schematically showing a compressor according to a first embodiment. 2 is a cross-sectional view of a compression mechanism of the compressor according to the first embodiment, schematically showing one end face side of a cylinder at top dead center. FIG. 3 is a cross-sectional view of the compression mechanism of the compressor according to the first embodiment, schematically showing the other end face side of the cylinder at top dead center. FIG. 2 is a cross-sectional view of a compression mechanism of the compressor according to the first embodiment, schematically showing one end face side of a cylinder at bottom dead center. FIG. 3 is a cross-sectional view of the compression mechanism of the compressor according to the first embodiment, schematically showing the other end face side of the cylinder at bottom dead center. FIG. 3 is a side view of the cylinder of the compressor according to the first embodiment, showing a schematic view of a portion in which a vane groove and a vane spring housing hole are formed. FIG. 2 is a longitudinal cross-sectional view of a cylinder of the compressor according to the first embodiment, schematically showing a portion in which a vane groove and a vane spring receiving hole are formed. FIG. 2 is a longitudinal cross-sectional view schematically illustrating a portion of the cylinder of the compressor according to the first embodiment where a suction port is formed. FIG. FIG. 2 is a top view schematically showing a vane of the compressor according to the first embodiment. FIG. 10 is a longitudinal cross-sectional view of the vane shown in FIG. 9 . 2 is a longitudinal cross-sectional view schematically illustrating a part of the compression mechanism of the compressor according to the first embodiment, in which a vane is positioned at a phase of top dead center. FIG. 2 is a longitudinal cross-sectional view schematically illustrating a part of the compression mechanism of the compressor according to the first embodiment, in which the vanes are positioned at the bottom dead center phase. FIG. FIG. 10 is a side view of a first modified example of the cylinder of the compressor according to the first embodiment, schematically showing a portion where a vane groove and a vane spring housing hole are formed. FIG. 10 is a side view of a second modified example of the cylinder of the compressor according to the first embodiment, schematically showing a portion where a vane groove and a vane spring housing hole are formed. FIG. 10 is a longitudinal cross-sectional view of a second modified example of the cylinder of the compressor according to the first embodiment, schematically showing a portion where a vane groove and a vane spring housing hole are formed. FIG. 4 is an explanatory diagram schematically illustrating a first modified example of a vane in the compressor according to the first embodiment. FIG. 17 is a longitudinal cross-sectional view of the vane shown in FIG. 16 . FIG. 10 is an explanatory diagram schematically illustrating a second modified example of the vane in the compressor according to the first embodiment. FIG. 10 is an explanatory diagram schematically illustrating a third modified example of the vane in the compressor according to the first embodiment. FIG. 10 is an explanatory diagram that schematically shows a fourth modified example of the vane in the compressor according to the first embodiment. 1 is a refrigeration circuit diagram of a refrigeration cycle device including a compressor according to a first embodiment. FIG. 10 is a cross-sectional view of a compression mechanism of a compressor according to a second embodiment, schematically showing the other end face side of a cylinder when a rolling piston is at top dead center. FIG. 10 is a cross-sectional view of the compression mechanism of the compressor according to the second embodiment, schematically showing the other end face side of the cylinder when the phase of the rolling piston is 90° with respect to the top dead center. FIG. 10 is a cross-sectional view schematically illustrating the other end face side of the cylinder, showing a modified example of the compression mechanism of the compressor according to the second embodiment. FIG. 10 is a side view of a cylinder of a compressor according to a second embodiment, schematically showing a portion in which a vane groove and a vane spring housing hole are formed. FIG. 11 is a longitudinal cross-sectional view schematically illustrating a cylinder of a compressor according to a third embodiment, with vanes positioned at the top dead center phase. FIG. 10 is a top view schematically showing a vane of a compressor according to a third embodiment. 28 is a cross-sectional view taken along the line CC shown in FIG. 27.

Embodiments of the present disclosure will be described below with reference to the drawings. Note that identical or corresponding parts in each drawing are designated by the same reference numerals, and their descriptions will be omitted or simplified as appropriate. Furthermore, the shape, size, and arrangement of the configurations shown in each drawing may be modified as appropriate.

Embodiment 1.
First, a compressor 100 according to the first embodiment will be described. FIG. 1 is a longitudinal cross-sectional view schematically illustrating the compressor 100 according to the first embodiment. FIG. 2 is a cross-sectional view schematically illustrating one end face side A of the cylinder 40 at top dead center, which is a compression mechanism 4 of the compressor 100 according to the first embodiment. FIG. 3 is a cross-sectional view schematically illustrating the other end face side B of the cylinder 40 at top dead center, which is a compression mechanism 4 of the compressor 100 according to the first embodiment. FIG. 4 is a cross-sectional view schematically illustrating one end face side A of the cylinder 40 at bottom dead center, which is a compression mechanism 4 of the compressor 100 according to the first embodiment. FIG. 5 is a cross-sectional view schematically illustrating the other end face side B of the cylinder 40 at bottom dead center, which is a compression mechanism 4 of the compressor 100 according to the first embodiment. FIG. 6 is a side view schematically illustrating a portion of the cylinder 40 of the compressor 100 according to the first embodiment, in which the vane groove 42 and the vane spring receiving hole 43 are formed. Fig. 7 is a longitudinal cross-sectional view of the cylinder 40 of the compressor 100 according to the first embodiment, schematically showing a portion where the vane groove 42 and the vane spring housing hole 43 are formed. Fig. 8 is a longitudinal cross-sectional view of the cylinder 40 of the compressor 100 according to the first embodiment, schematically showing a portion where the suction port 40a is formed.

The compressor 100 according to the first embodiment is a fluid machine that draws in low-temperature, low-pressure refrigerant, compresses the drawn refrigerant, and discharges high-temperature, high-pressure refrigerant to the outside. The compressor 100 shown in FIG. 1 is, as an example, a single rotary compressor having one cylinder 40. The compressor 100 is not limited to a single rotary compressor, but may be a rotary compressor having multiple cylinders 40, such as a twin rotary compressor having two cylinders 40, or may have another structure. In addition, a compressor that flows a high flow rate of refrigerant requires effectively reducing pressure loss in the refrigerant intake path, so a twin rotary compressor with a high flow rate and high capacity is preferred.

As shown in FIG. 1, the compressor 100 according to the first embodiment comprises a sealed container 1 forming an outer shell, an electric motor unit 2 having a stator 20 and a rotor 21, a rotating shaft 3 that transmits the driving force of the electric motor unit 2, and a compression mechanism unit 4 that compresses a refrigerant by the driving force transmitted from the rotating shaft 3. The electric motor unit 2, the rotating shaft 3, and the compression mechanism unit 4 are housed inside the sealed container 1. The electric motor unit 2 is housed in an upper part inside the sealed container 1. The compression mechanism unit 4 is housed in a lower part inside the sealed container 1. The electric motor unit 2 and the compression mechanism unit 4 are connected via the rotating shaft 3.

The sealed container 1 is composed of an upper container 10 and a lower container 11. Note that the sealed container 1 is not limited to being formed from two components, the upper container 10 and the lower container 11, but may be formed from three or more components.

As shown in FIG. 1, the sealed container 1 is connected to the suction muffler 101 via a refrigerant suction pipe 12, and gas refrigerant is drawn into the sealed container 1 through the suction muffler 101. The suction muffler 101 is fixed to the outer surface of the lower container 11 of the sealed container 1 by welding or other means. The suction muffler 101 separates the low-temperature, low-pressure refrigerant sent from the refrigeration circuit into liquid refrigerant and gas refrigerant, prevents the liquid refrigerant from being drawn into the compression mechanism 4 as much as possible, and stores the separated liquid refrigerant. If liquid refrigerant flows into the compression mechanism 4 of the compressor 100 and is compressed, it could cause the compression mechanism 4 to malfunction. The suction muffler 101 also functions as a silencer, reducing or eliminating noise generated by the inflowing refrigerant.

A refrigerant discharge pipe 13, which discharges compressed refrigerant, is connected to the top of the sealed container 1. The refrigerant discharge pipe 13 is a refrigerant piping that discharges high-pressure gas refrigerant to the outside of the sealed container 1. The refrigerant discharge pipe 13 passes through the upper container 10 that constitutes the sealed container 1, and is joined to the upper container 10 by, for example, brazing or resistance welding.

The interior of the sealed container 1 is filled with high-temperature, high-pressure gas refrigerant compressed by the compression mechanism 4, and refrigeration oil 14 used to lubricate the compression mechanism 4 is stored at the bottom. The refrigeration oil 14 is used primarily to lubricate the sliding parts of the compression mechanism 4. An oil pump (not shown) is provided at the bottom of the rotating shaft 3. As the rotating shaft 3 rotates, the oil pump draws up the refrigeration oil 14 stored at the bottom of the sealed container 1 and supplies it to each sliding part of the compression mechanism 4. Mechanical lubrication of the compression mechanism 4 is ensured by the supply of oil to each sliding part.

As shown in Figure 1, the electric motor unit 2 has a cylindrical stator 20 fixed to the inner wall surface of the sealed container 1 by shrink fitting or the like, and a cylindrical rotor 21 rotatably disposed opposite the inner surface of the stator 20 and rotates by magnetic action. A rotating shaft 3 is fitted into the center of the rotor 21. The electric motor unit 2 generates a rotational driving force in the rotating shaft 3 using power supplied from an external power source, and transmits the rotational driving force to the compression mechanism unit 4 via the rotating shaft 3. The electric motor unit 2 may be, for example, a brushless DC motor.

The rotating shaft 3 has a main shaft portion 30 fixed to the rotor 21 of the electric motor portion 2, a counter shaft portion 31 provided on the opposite side of the main shaft portion 30 across the compression mechanism portion 4, and an eccentric shaft portion 32 provided between the main shaft portion 30 and the counter shaft portion 31. The rotating shaft 3 is formed in the axial direction from above to below the sealed container 1, with the main shaft portion 30, eccentric shaft portion 32, and counter shaft portion 31 formed in that order. The main shaft portion 30 is fitted into the center of the rotor 21 of the electric motor portion 2 and fixed by shrink fitting or press fitting. The central axis of the eccentric shaft portion 32 is eccentric with respect to the central axes of the main shaft portion 30 and the counter shaft portion 31.

The compression mechanism 4 compresses the low-pressure gas refrigerant drawn into the low-pressure space of the sealed container 1 from the refrigerant suction pipe 12 into high-pressure gas refrigerant using the rotational driving force supplied from the electric motor 2. The high-pressure gas refrigerant compressed by the compression mechanism 4 is discharged into the sealed container 1 from above the compression mechanism 4. As shown in Figures 1 to 8, the compression mechanism 4 includes a cylinder 40, an upper bearing 44, a lower bearing 45, a discharge muffler 46, a rolling piston 47, a vane 48, and a vane spring 49.

The outer periphery of the cylinder 40 is fixed to the sealed container 1 with bolts or the like. As shown in Figure 1, the upper surface of the cylinder 40 is one end surface side A, and the lower surface is the other end surface side B. As shown in Figures 2 to 5, the cylinder 40 has a hollow cylindrical shape, and the hollow interior forms a cylinder chamber 41. As shown in Figure 1, the cylinder chamber 41 is open at both ends in the axial direction of the rotating shaft 3, and is closed by an upper bearing 44 provided on the upper surface of the cylinder 40 and a lower bearing 45 provided on the lower surface of the cylinder 40. In other words, the cylinder chamber 41 is a space surrounded by the inner circumferential surface of the cylinder 40, the inner wall surface of the upper bearing 44, and the inner wall surface of the lower bearing 45.

As shown in Figures 2 to 5 and 8, the cylinder 40 is provided with an intake port 40a, which penetrates from the outer surface to the cylinder chamber 41, through which gas refrigerant passes from the refrigerant intake pipe 12. The intake port 40a connects the refrigerant intake pipe 12 and the cylinder chamber 41.

As shown in Figures 2 to 7, the cylinder 40 is formed with a vane groove 42 that communicates with the cylinder chamber 41 and extends in the radial direction r centered on the rotary shaft 3. As shown in Figures 2 to 5, the vane groove 42 penetrates the cylinder 40 in the axial direction from one end face side A to the other end face side B when viewed from the direction in which the outer shape of the cylinder 40 appears circular. A vane 48 that divides the cylinder chamber 41 into a suction chamber 41a and a compression chamber 41b is slidably fitted into the vane groove 42. The suction chamber 41a is a low-pressure space that communicates with the suction port 40a. The compression chamber 41b is a high-pressure space that communicates with a discharge port 44a (see Figure 1) for discharging air to the outside of the cylinder chamber 41.

A stop portion 42a is formed at the end of the vane groove 42 on the outer peripheral surface of the cylinder 40. The stop portion 42a is provided to stop the movement of the vane 48 toward the outer peripheral surface of the cylinder 40 and limit the movement of the vane 48 so that the vane 48 does not protrude from the outer peripheral surface of the cylinder 40. The stop portion 42a also functions as a back pressure chamber for introducing high-pressure refrigerant. As shown in Figures 2 and 4, the stop portion 42a has an arc shape that opens only to the vane groove 42 when viewed from one end face side A of the cylinder 40.

As shown in Figures 6 and 7, the cylinder 40 is formed with a vane spring storage hole 43 as a space for storing and operating the vane spring 49. The vane spring storage hole 43 is formed to extend in the radial direction r of the cylinder 40. As shown in Figure 7, the vane spring storage hole 43 penetrates the outer peripheral surface of the cylinder 40 but does not penetrate the inner peripheral surface of the cylinder 40. The length of the vane spring storage hole 43 is determined according to the shape of the vane spring 49 to be operated or the shape of the cylinder 40.

As shown in Figure 1, the upper bearing 44 is formed in a roughly inverted T-shape in side view. The upper bearing 44 is provided on one end face of the cylinder 40 on the side where the electric motor unit 2 is located, and closes one axial opening of the cylinder chamber 41. The upper bearing 44 is also fitted onto the main shaft portion 30 of the rotating shaft 3, and rotatably supports the main shaft portion 30. The upper bearing 44, together with the lower bearing 45, is fixed to the cylinder 40 by a common screw 5.

The upper bearing 44 is formed with a discharge port 44a for discharging the refrigerant compressed in the compression chamber 41b to the outside of the cylinder chamber 41. A discharge valve (not shown) is attached to the discharge port 44a. The discharge valve is controlled to time the high-temperature, high-pressure gas refrigerant to be discharged from the compression chamber 41b through the discharge port 44a. Specifically, the discharge valve closes the discharge port 44a when the pressure inside the compression chamber 41b is lower than the pressure inside the sealed container 1. Furthermore, when the pressure inside the compression chamber 41b becomes higher than the pressure inside the sealed container 1, the discharge valve is pushed upward by the pressure inside the compression chamber 41b.

As shown in Figure 1, the lower bearing 45 is formed in a roughly T-shape when viewed from the side. The lower bearing 45 is provided on the other end face of the cylinder 40 opposite the side on which the electric motor unit 2 is located, and closes the other axial opening of the cylinder chamber 41. The lower bearing 45 is also fitted onto the countershaft portion 31 of the rotating shaft 3, and rotatably supports the countershaft portion 31.

As shown in Figure 1, the discharge muffler 46 is attached so as to cover the outside of the upper bearing 44. Inside the compression chamber 41b, the operations of drawing in, compressing, and discharging refrigerant are repeated. The compressed gas refrigerant is intermittently discharged from the discharge port 44a. This may cause noise such as pulsating sounds to be generated from the cylinder 40. The discharge muffler 46 is provided to suppress noise such as pulsating sounds generated from the cylinder 40.

The discharge muffler 46 also has a discharge hole (not shown) that connects the space formed by the discharge muffler 46 and the upper bearing 44 to the interior of the sealed container 1. The gas refrigerant discharged from the cylinder 40 through the discharge port 44a is first discharged into the space formed by the discharge muffler 46 and the upper bearing 44, and then discharged from the discharge hole into the interior of the sealed container 1.

As shown in Figures 2 to 5, the rolling piston 47 is formed in a hollow cylindrical shape, with the eccentric shaft portion 32 of the rotating shaft 3 slidably fitted into the hollow interior. The rolling piston 47 is housed in the cylinder chamber 41 together with the eccentric shaft portion 32. When the rotating shaft 3 is rotated by the drive of the electric motor unit 2, the rolling piston 47 rotates along the inner surface of the cylinder chamber 41, compressing the refrigerant.

As shown in Figures 2 to 5, during the refrigerant compression process, the vane 48 slides back and forth inside the vane groove 42 following the rotation of the rolling piston 47, with its tip abutting the outer surface of the rolling piston 47. The cylinder chamber 41 is divided into a suction chamber 41a and a compression chamber 41b when the tip of the vane 48 abuts the outer surface of the rolling piston 47. The vane 48 is made of, for example, a non-magnetic material.

The vane spring 49 abuts against the back side of the vane 48 and presses against the vane 48 so that the tip of the vane 48 abuts against the outer peripheral surface of the rolling piston 47. The vane spring 49 is housed in the vane spring housing hole 43 of the cylinder 40 and is arranged in series with the vane 48. As shown in Figure 7, the vane spring 49 is fixed to the cylinder 40 by the end coil 49a, which is press-fitted inside the vane spring housing hole 43, abutting against the inner wall surface of the vane spring housing hole 43. Note that the method for fixing the vane spring 49 to the cylinder 40 is not limited to this method.

In the compression mechanism 4 configured as described above, high-pressure gas refrigerant inside the sealed container 1 flows into the stop portion 42a, and the pressure difference between the pressure of the gas refrigerant at the stop portion 42a and the pressure of the gas refrigerant in the cylinder chamber 41 creates a force that moves the vane 48 in the radial direction r toward the center of the cylinder chamber 41. Note that in the compression mechanism 4, the pressure difference between the pressure of the gas refrigerant at the stop portion 42a and the pressure of the gas refrigerant inside the cylinder chamber 41 may not be sufficient to press the vane 48 against the outer peripheral surface of the rolling piston 47. Even in such cases, the compression mechanism 4 can use the force of the vane spring 49 to press the vane 48 toward the rolling piston 47, so the tip of the vane 48 can always abut against the outer peripheral surface of the rolling piston 47.

Now, the operation of the compressor 100 will be explained. In the compressor 100, the rotating shaft 3 is rotated by the drive of the electric motor unit 2, causing the rolling piston 47 to rotate together with the eccentric shaft unit 32 inside the cylinder chamber 41. In the cylinder chamber 41, the suction chamber 41a separated by the vane 48 increases in volume as the rotating shaft 3 rotates. In the cylinder chamber 41, the compression chamber 41b separated by the vane 48 decreases in volume.

In the compressor 100, the suction chamber 41a and suction port 40a are connected, and low-pressure gas refrigerant is drawn into the cylinder chamber 41. Next, the communication between the compression chamber 41b and suction port 40a is closed by the rolling piston 47, and the volume of the compression chamber 41b decreases, compressing the gas refrigerant inside the compression chamber 41b. Finally, the compression chamber 41b is connected to the discharge port 44a of the upper bearing 44, and after the gas refrigerant inside the compression chamber 41b reaches a predetermined pressure, the discharge valve provided in the discharge port 44a opens, and the compressed, high-pressure, high-temperature gas refrigerant is discharged outside the cylinder chamber 41.

The high-pressure, high-temperature gas refrigerant discharged outside the cylinder chamber 41 is discharged into the sealed container 1 via the discharge muffler 46. The discharged gas refrigerant then passes through the motor section 2, rises inside the sealed container 1, and is discharged outside the sealed container 1 from the refrigerant discharge pipe 13 located at the top of the sealed container 1. The refrigerant discharged outside the sealed container 1 circulates through the refrigeration circuit and returns to the suction muffler 101.

In recent years, as one of the measures to combat global warming, low GWP (Global Warming Potential) refrigerants, such as R32, R1234yf, or R290, have been used as refrigerants in refrigeration cycle devices equipped with compressors. However, low GWP refrigerants have lower refrigeration capacity per volume compared to traditional refrigerants such as R410A. For this reason, in refrigeration cycle devices, the flow rate of refrigerant flowing through the device must be increased to achieve the desired refrigeration capacity. Increasing the stroke volume of the compression chamber 41b is an effective way to increase the refrigerant flow rate. The stroke volume is the amount of refrigerant discharged per rotation by the compression mechanism 4. To increase this stroke volume, it is desirable to enlarge the inner diameter of the cylinder chamber 41.

However, increasing the inner diameter of the cylinder chamber 41 increases the amount by which the vane 48 protrudes into the cylinder chamber 41. If the vane 48 protrudes too far into the cylinder chamber 41 relative to its overall length, its operation becomes unstable and its ability to follow the rolling piston 47 deteriorates. As a result, the compressor 100 may experience refrigerant leakage from the compression chamber 41b (high pressure) to the suction chamber 41a (low pressure) in the cylinder chamber 41, reducing compression efficiency. Furthermore, the side area of the vane 48, which supports the load of the refrigerant differential pressure acting from the compression chamber 41b to the suction chamber 41a, becomes smaller, resulting in harsh sliding conditions and causing seizure, which could lead to failure of the compressor 100.

Therefore, in the compressor 100 of this embodiment 1, the inner diameter of the cylinder chamber 41 of the cylinder 40 is enlarged, so that even if the amount of protrusion of the vane 48 into the cylinder chamber 41 increases, refrigerant leakage from the high-pressure chamber to the low-pressure chamber and seizure can be suppressed.

Specifically, as shown in Figures 2 to 7, the vane groove 42 has an opening 42b at one end located on the inner periphery of the cylinder 40. Furthermore, as shown in Figures 2 and 3, the vane groove 42 does not penetrate all the way to the outer periphery of the cylinder 40 on one end face side A of the cylinder 40, which is the upper surface of the cylinder 40, but has a stop portion 42a for the vane 48 at the end on the outer periphery side of the cylinder 40. On the other hand, as shown in Figures 4 and 5, the vane groove 42 penetrates the outer periphery of the cylinder 40 on the other end face side B of the cylinder 40, which is the lower surface of the cylinder 40. In other words, only the one end face side A of the cylinder 40 functions as the stop portion 42a of the vane groove 42. As shown in Figure 6, the vane spring storage hole 43 has a cross-sectional shape perpendicular to the extension direction of the vane spring storage hole 43 that is a perfect circle, and the vane grooves 42 on the other end face side B of the cylinder 40 are connected. In the illustrated example, one end surface side A is the upper surface of the cylinder 40 and the other end surface side B is the lower surface of the cylinder 40, but one end surface side A may be the lower surface of the cylinder 40 and the other end surface side B may be the upper surface of the cylinder 40.

Figure 9 is a top view schematically showing the vane 48 of the compressor 100 according to embodiment 1. Figure 10 is a longitudinal cross-sectional view of the vane 48 shown in Figure 9. Figure 11 is a longitudinal cross-sectional view schematically showing a part of the compression mechanism 4 of the compressor 100 according to embodiment 1, in which the vane 48 is positioned at the top dead center phase. Figure 12 is a longitudinal cross-sectional view schematically showing a part of the compression mechanism 4 of the compressor 100 according to embodiment 1, in which the vane 48 is positioned at the bottom dead center phase.

As shown in Figures 9 to 12, the length Lb of the vane 48 along the radial direction r at the portion 482 located on the other end surface B of the cylinder 40 penetrating the outer peripheral surface is longer than the length La of the portion 481 located on the one end surface side A of the cylinder 40 where the stop portion 42a is formed. In other words, the vane 48 has a non-rectangular shape. The length of the vane 48 is determined by the structure of the cylinder 40. As shown in Figures 2, 3, and 11, the vane 48, which follows the rolling piston 47, does not protrude from the inner peripheral surface of the cylinder chamber 41 and is completely housed in the vane groove 42 when the rolling piston 47 is positioned at the top dead center phase. The top dead center phase occurs when the rolling piston 47 is positioned at the phase of the vane groove 42, as shown in Figures 2, 3, and 11. At the top dead center phase, as long as the vane 48 follows the rolling piston 47, the back side of the vane 48 does not come into contact with the stop portion 42a at a portion 481 located on one end face side A of the cylinder 40, and does not protrude outward from the outer circumferential surface of the cylinder 40 at a portion 482 located on the other end face side B of the cylinder 40.

Furthermore, the vane 48 is sized so that it does not protrude outward from the outer circumferential surface of the cylinder 40 when it is spaced apart from the rolling piston 47 and pressed against the stop portion 42a. When liquid refrigerant is drawn into the cylinder chamber 41, the vane 48 temporarily stops following the rolling piston 47 to prevent damage or failure of components of the compression mechanism 4 due to overload caused by liquid compression. At this time, the back side of the vane 48 at one end face side A of the cylinder 40 is pressed against the stop portion 42a by the pressure from the high-pressure liquid refrigerant. At this time, as described above, the back side of the vane 48 at the portion 482 located at the other end face side B of the cylinder 40 does not protrude outward from the outer circumferential surface of the cylinder 40. By ensuring that the vane 48 does not protrude outward from the outer circumferential surface of the cylinder 40 using the stop portion 42a, the vane 48 can be prevented from coming into contact with the sealed container 1. This makes it possible to prevent the compressor 100 from exploding due to scraping or deformation of the inside of the sealed container 1, thereby ensuring safety.

4, 5 and 12, when the rolling piston 47 is positioned at the bottom dead center phase, the vane 48 following the rolling piston 47 protrudes from the inner circumferential surface of the cylinder chamber 41. The bottom dead center phase is when the rolling piston 47 has revolved 180° from the top dead center and is positioned at the phase opposite to the vane groove 42. At this time, the amount of protrusion of the vane 48 from the inner circumferential surface of the cylinder chamber 41 is geometrically defined to be twice the eccentricity e of the eccentric shaft portion 32 that determines the orbit of the rolling piston 47. When the inner diameter of the cylinder 40 is R and the outer diameter of the rolling piston 47 is r, the eccentricity e is expressed as follows:
e = R/2 - r/2
Here, in the compressor 100 according to the first embodiment, when the overall length of the vane 48 at the portion 482 located on the other end face side B of the cylinder 40 is Lb,
2e/Lb<0.5
That is, the ratio (protrusion rate) of the amount of protrusion of the vane 48 into the cylinder chamber 41 to the total length is set to less than 50%. This setting allows the sliding reciprocating motion of the vane 48 to be kept stable. Therefore, the compressor 100 can ensure a long total length of the vane 48 and increase the amount of protrusion of the vane 48, thereby achieving high flow rate, high capacity, and high reliability. The length La of the vane 48 on one end face side A of the cylinder 40 is set as follows:
2e/La≧0.5
Or you can say,
2e/La<0.5
It may also be possible to use the following.

Figure 13 is a side view of a first variant of the cylinder 40 of the compressor 100 according to embodiment 1, schematically illustrating the portion where the vane groove 42 and vane spring storage hole 43 are formed. As shown in Figure 13, the vane spring storage hole 43 may be formed by offsetting the central axis P from the center O of the cylinder 40 in the thickness direction toward one end face side A of the cylinder 40. This offset direction is the direction in which the length of the stop portion 42a becomes shorter. The length of the vane 48 along the radial direction r of the cylinder 40 is longer at the portion 482 located on the other end face side B of the cylinder 40 than at the portion 481 located on the one end face side A of the cylinder 40. Therefore, the side area of the vane 48 can be increased by shortening the length of the stop portion 42a formed on the one end face side A of the cylinder 40. By increasing the side area of the vane 48, the compressor 100 can adequately support the pressure difference between the high-pressure refrigerant and the low-pressure refrigerant, thereby further improving reliability.

14 is a side view of modified example 2 of the cylinder 40 of the compressor 100 according to embodiment 1, schematically illustrating the portion where the vane groove 42 and vane spring storage hole 43 are formed. FIG. 15 is a longitudinal cross-sectional view of modified example 2 of the cylinder 40 of the compressor 100 according to embodiment 1, schematically illustrating the portion where the vane groove 42 and vane spring storage hole 43 are formed. As shown in FIGS. 14 and 15 , when the stop portion 42a is projected onto the other end surface B of the cylinder 40 as viewed from one end surface A of the cylinder 40, the groove width L1 of the vane groove 42 in the interval X from the point 420a where the stop portion 42a is projected to the outer peripheral surface of the cylinder 40 is larger than the groove width L2 of the vane groove 42 in the interval Y from the point 420a where the stop portion 42a is projected to the inner peripheral surface of the cylinder 40. This facilitates machining of the vane groove 42. The point 420a where the stop portion 42a is projected may be anywhere within the range of the projected point 420a.

The vane groove 42 must be formed to a flatness of less than 10 μm, requiring high machining precision. Therefore, it is difficult to machine the vane groove 42 with the same flatness from the inner circumferential surface to the outer circumferential surface of the cylinder 40. However, machining the vane groove 42 is easier if the plane X between the projected point 420a of the stop portion 42a and the outer circumferential surface of the cylinder 40 and the plane Y between the projected point 420a of the stop portion 42a and the inner circumferential surface of the cylinder 40 are formed as separate planes. Here, the vane 48 and vane groove 42 experience the most severe sliding conditions when the rolling piston 47 is at bottom dead center. However, the section X between the projected point 420a of the stop portion 42a and the outer circumferential surface of the cylinder 40 contributes little to the sliding conditions. Therefore, even if the compressor 100 is processed such that the plane X between the point 420a where the stop portion 42a is projected and the outer peripheral surface of the cylinder 40 and the sliding surface Y between the point 420a where the stop portion 42a is projected and the inner peripheral surface of the cylinder 40 are separate planes, there is little effect on the sliding conditions.

Figure 16 is an explanatory diagram schematically illustrating a first variant of the vane 48 in the compressor 100 according to embodiment 1. Figure 17 is a longitudinal cross-sectional view of the vane 48 shown in Figure 16. As shown in Figures 16 and 17, the vane 48 may be configured such that an inlet groove 48a for introducing high-pressure gas refrigerant is formed in the end face of the portion 482 located on the other end face side B of the cylinder 40. The inlet groove 48a is formed along the radial direction r of the cylinder 40. The vane 48 has an asymmetric structure between the portion 481 located on one end face side A of the cylinder 40 and the portion 482 located on the other end face side B. This results in unbalanced reciprocating motion during operation, which can cause localized contact at the sliding points, resulting in seizure and galling. By providing the inlet groove 48a for the high-pressure gas refrigerant, the vane 48 can apply load from above and below the cylinder 40, improving the balance of the overall reciprocating motion. The introduction groove 48a communicates with the back side of the vane 48, but does not communicate with the tip side that comes into contact with the rolling piston 47. If the introduction groove 48a communicated with the tip side, the high-pressure gas refrigerant outside the compression mechanism 4 would communicate with the low-pressure refrigerant inside the compression chamber 41b, reducing the efficiency of the compressor 100. The vane 48 may be configured so that the introduction groove 48a is formed in an end surface of a portion 481 located on one end surface side A of the cylinder 40, or so that the introduction groove 48a is formed in both end surface surfaces of the portion 481 located on one end surface side A and the portion 482 located on the other end surface side B of the cylinder 40.

Figure 18 is an explanatory diagram that schematically illustrates a second variant of the vane 48 in the compressor 100 according to embodiment 1. Figure 19 is an explanatory diagram that schematically illustrates a third variant of the vane 48 in the compressor according to embodiment 1. The vane 48 shown in Figure 18 has an R-shaped back surface 48b at the portion 481 located on one end face side A of the cylinder 40 where the stop portion 42a is formed. In the compressor 100 according to embodiment 1, the stop portion 42a is provided only on one end face side A of the cylinder 40. Therefore, the stop portion 42a has a shorter length that receives the vane 48 compared to conventional compressors. Therefore, when the back surface of the vane 48 collides with the stop portion 42a, the generated stress is large, making parts more likely to be chipped or worn. On the other hand, by forming the R-shaped back surface of the vane 48 into 48b, localized stress due to corner impact is suppressed, thereby suppressing chipping or wear of parts. As shown in FIG. 19, the vane 48 may have only the corners 48b on the back surface of a portion 481 located on one end face side of the cylinder 40 where the stop portion 42a is formed.

Figure 20 is an explanatory diagram schematically illustrating a fourth variant of the vane 48 in the compressor 100 according to embodiment 1. The vane 48 shown in Figure 20 has a central portion 483 extending along the radial direction r of the cylinder 40 between a portion 481 located on one end face side A of the cylinder 40 and a portion 482 located on the other end face side B. The central portion 483 is configured to fit inside the vane spring 49, and when the rolling piston 47 is in the top dead center phase, its back surface is located closer to the outer circumferential surface of the cylinder 40 than the end turn 49a of the vane spring 49. The vane 48 shown in Figure 20 has a central portion 483, which increases the lateral area and therefore can adequately support the load of the refrigerant differential pressure acting from the compression chamber 41b (high pressure) to the suction chamber 41a (low pressure).

Here, the dimensions of the cylinder 40 in the compressor 100 according to the first embodiment will be described. Note that the dimensions of the cylinder 40 shown below are examples and are not limited to these dimensions. The thickness of the cylinder 40 is, for example, 30 mm. The outer diameter of the cylinder 40 is 130 mm. The inner diameter of the cylinder 40 is 60 mm. The difference in radius between the inner and outer diameters of the cylinder 40 is 35 mm. The diameter of the vane spring storage hole 43 is 14 mm. The width of the vane groove 42 and the vane 48 is 4 mm. The clearance formed by the vane groove 42 and the vane 48 is 30 μm.

The diameter of the stop portion 42a is 9 mm. If the center of the vane spring storage hole 43 is aligned with the center of the cylinder 40, the length of the stop portion 42a is (cylinder 40 thickness 30 mm - spring diameter 14 mm) ÷ 2 = 8 mm. As shown in Figure 13, if the center of the vane spring storage hole 43 is offset toward one end face side A by 2 mm, the length of the stop portion 42a is reduced by that amount to 6 mm. Furthermore, as shown in Figures 16 and 17, if an introduction groove 48a is formed in the vane 48, the width of the vane 48 is 4 mm, while the introduction groove 48a has a width of 2 mm and a depth of 1 mm.

The overall length of the vane 48 is such that the length La of the portion 481 located on one end face side A of the cylinder 40 is 30 mm, and the length Lb of the portion 482 located on the other end face side B of the cylinder 40 is 34.4 mm. At top dead center when the vane 48 is following the rolling piston 47, the distance between the stop portion 42a and the back surface of the vane 48 is 0.5 mm. Therefore, as long as the vane 48 maintains its following of the rolling piston 47, the vane 48 does not come into contact with the stop portion 42a. Even if the vane 48 ceases to follow the rolling piston 47 and the back surface of the vane 48 comes into contact with the stop portion 42a, the back surface of the portion 482 located on the other end face side B of the cylinder 40 does not protrude outward from the outer circumferential surface of the cylinder 40.

As described above, the compressor 100 according to the first embodiment comprises a sealed container 1 forming an outer shell, an electric motor unit 2 having a stator 20 and a rotor 21, a rotating shaft 3 connected to the rotor 21 and transmitting the driving force of the electric motor unit 2, and a compression mechanism unit 4 connected to the rotating shaft 3 and compressing a refrigerant using the driving force transmitted from the rotating shaft 3. The rotating shaft 3 has an eccentric shaft portion 32. The compression mechanism unit 4 comprises a cylinder 40 fixed to the sealed container 1 and having a cylinder chamber 41 into which a refrigerant is drawn and compressed, a rolling piston 47 fitted to the eccentric shaft portion 32 and housed in the cylinder chamber 41, rotating together with the eccentric shaft portion 32 to compress the refrigerant, and a vane 48 disposed in a vane groove 42 formed in the radial direction r of the cylinder 40 and following the rolling piston 47 to divide the cylinder chamber 41 into a refrigerant suction chamber 41a and a compression chamber 41b. The vane groove 42 does not penetrate all the way to the outer circumferential surface of the cylinder 40 at one end face side A of the two opposing end faces of the cylinder 40, but has a stop portion 42a for the vane 48 formed at the end on the outer circumferential surface side of the cylinder 40, and is formed to penetrate the outer circumferential surface of the cylinder 40 at the other end face side B of the cylinder 40. The vane 48 is configured such that a length Lb along the radial direction r of a portion 482 located on the other end face side B of the cylinder 40 is longer than a length La along the radial direction r of a portion 481 located on the one end face side A of the cylinder 40.

Therefore, according to the compressor 100 of this embodiment 1, the amount of protrusion of the vane 48 into the cylinder chamber 41 relative to the overall length of the vane 48 can be reduced, and the side area of the vane 48 can be increased. Therefore, even if the inner diameter of the cylinder chamber 41 of the cylinder 40 is enlarged and the amount of protrusion of the vane 48 is increased, refrigerant leakage and seizure from the high-pressure compression chamber 41b to the low-pressure suction chamber 41a can be suppressed.

Next, a refrigeration cycle device 200 equipped with a compressor 100 according to embodiment 1 will be described with reference to Figure 21. Figure 21 is a refrigeration circuit diagram of a refrigeration cycle device 200 equipped with a compressor 100 according to embodiment 1.

As shown in Figure 21, the refrigeration cycle device 200 of this embodiment 1 has a refrigeration circuit 107 in which a compressor 100, a flow path switching device 102, an outdoor heat exchanger 103, an expansion mechanism 104, an indoor heat exchanger 105, and an intake muffler 101 are connected in sequence by refrigerant piping 106, and in which the refrigerant circulates.

The refrigerant flowing through the refrigeration circuit 107 is R407C refrigerant, R410A refrigerant, R32 refrigerant, etc. The efficiency of the compressor 100 can be further improved by using a low GWP refrigerant such as R1234yf refrigerant or R290 refrigerant.

The flow path switching device 102 is, for example, a four-way valve that has the function of switching the refrigerant flow path. During cooling operation, the flow path switching device 102 connects the refrigerant discharge side of the compressor 100 to the gas side of the outdoor heat exchanger 103, and switches the refrigerant flow path to connect the refrigerant suction side of the compressor 100 to the gas side of the outdoor heat exchanger 105. On the other hand, during heating operation, the flow path switching device 102 connects the refrigerant discharge side of the compressor 100 to the gas side of the indoor heat exchanger 105, and switches the refrigerant flow path to connect the refrigerant suction side of the compressor 100 to the gas side of the outdoor heat exchanger 103. Note that the flow path switching device 102 may be configured using a combination of two-way or three-way valves.

The outdoor heat exchanger 103 functions as a condenser during cooling operation, exchanging heat between the refrigerant discharged from the compressor 100 and flowing inside and the outdoor air. The outdoor heat exchanger 103 also functions as an evaporator during heating operation, exchanging heat between the refrigerant flowing out of the expansion mechanism 104 and flowing inside and the outdoor air. The outdoor heat exchanger 103 draws in outdoor air using a blower (not shown), and discharges the air that has exchanged heat with the refrigerant to the outside.

The expansion mechanism 104 reduces the pressure of the refrigerant flowing out of the condenser and expands it, and is composed, for example, of an electronic expansion valve whose throttle opening can be adjusted. The expansion mechanism 104 controls the pressure of the refrigerant flowing into the outdoor heat exchanger 103 or the indoor heat exchanger 105 by adjusting the opening.

The indoor heat exchanger 105 functions as an evaporator during cooling operation, exchanging heat between the refrigerant flowing through the expansion mechanism 104 and the indoor air. The indoor heat exchanger 105 also functions as a condenser during heating operation, exchanging heat between the refrigerant flowing through the interior and the indoor air. The indoor heat exchanger 105 draws in indoor air using a blower (not shown), and supplies the air that has exchanged heat with the refrigerant into the room.

Next, the operation of the refrigeration cycle unit 200 during heating operation will be described. During heating operation of the air conditioner, the pipes connected to the flow path switching device 102 are connected to form a circuit on the solid line side of Figure 21. The high-temperature, high-pressure gas refrigerant discharged from the compressor 100 passes through the flow path switching device 102 and flows to the indoor heat exchanger 105, where it exchanges heat with the air and condenses and liquefies. The condensed and liquefied refrigerant is decompressed by the expansion mechanism 104, becoming a low-temperature, low-pressure two-phase gas-liquid refrigerant, which then flows to the outdoor heat exchanger 103, where it exchanges heat with the air and gasifies. The gasified refrigerant passes through the flow path switching device 102 and is drawn into the compressor 100 via the suction muffler 101.

Next, the operation of the refrigeration cycle unit 200 during cooling operation will be described. When the air conditioner is operating in cooling mode, the pipes connected to the flow path switching device 102 are connected to form a circuit on the dashed line side of Figure 21. The high-temperature, high-pressure gas refrigerant discharged from the compressor 100 passes through the flow path switching device 102 and flows to the outdoor heat exchanger 103, where it exchanges heat with the air and condenses and liquefies. The condensed and liquefied refrigerant is decompressed by the expansion mechanism 104, becoming a low-temperature, low-pressure two-phase gas-liquid refrigerant, which then flows to the indoor heat exchanger 105, where it exchanges heat with the air and gasifies. The gasified refrigerant passes through the flow path switching device 102 and is drawn into the compressor 100 via the suction muffler 101.

The refrigeration cycle device 200 is equipped with the compressor 100 according to embodiment 1. Therefore, the refrigeration cycle device 200 can achieve the same effects as the compressor 100 according to embodiment 1.

Embodiment 2.
Next, a compressor 100 according to a second embodiment will be described with reference to FIGS. 22 to 25. FIG. 22 is a cross-sectional view of the compression mechanism 4 of the compressor 100 according to the second embodiment, schematically showing the other end face side B of the cylinder 40 when the rolling piston 47 is at top dead center. FIG. 23 is a cross-sectional view of the compression mechanism 4 of the compressor 100 according to the second embodiment, schematically showing the other end face side B of the cylinder 40 when the phase of the rolling piston 47 is 90° relative to top dead center. FIG. 24 is a cross-sectional view of a modified compression mechanism 4 of the compressor 100 according to the second embodiment, schematically showing the other end face side B of the cylinder 40. FIG. 25 is a side view of the cylinder 40 of the compressor 100 according to the second embodiment, schematically showing a portion where the vane groove 42 and the vane spring receiving hole 43 are formed. Note that the same components as those of the compressor 100 described in the first embodiment are designated by the same reference numerals, and their description will be omitted as appropriate.

As shown in Figures 22 and 23, the sealed container 1 has a through hole 10a formed at a position corresponding to the vane groove 42, through which the vane 48 can slide. The through hole 10a is blocked from the outer peripheral surface of the sealed container 1 by a blocking part 15, which is a separate part from the sealed container 1. The rest of the configuration is the same as that of the compressor 100 described in embodiment 1 above.

As shown in Figure 22, when the rolling piston 47 is positioned at the top dead center phase, the portion of the vane 48 located on the other end face side B of the cylinder 40 protrudes from the outer peripheral surface of the cylinder 40 into the through-hole 10a. By allowing the vane 48 to protrude from the outer peripheral surface of the cylinder 40, the length of the vane 48 in the radial direction r of the cylinder 40 can be increased. By increasing the overall length of the vane 48, the compressor 100 can relax the sliding conditions between the vane 48 and the vane groove 42, thereby reducing pressure loss, improving compressor efficiency, and further enhancing reliability.

Note that the compressor 100 according to embodiment 2 is not limited to a configuration in which a through hole 10a is formed in the sealed container 1. As shown in FIG. 24, a configuration equivalent to the through hole 10a may be achieved by performing pressing or the like to form a recess 10b in the inner wall surface of the sealed container 1, against which the vane 48 can slide. When the rolling piston 47 is positioned at the top dead center phase, the vane 48 protrudes from the outer peripheral surface of the cylinder 40 into the recess 10b.

In addition, in the compressor 100 according to the second embodiment, it is necessary to increase the overall length of the vane 48 to increase the force of the vane spring 49 pressing against the vane 48. If the pressing load of the vane spring 49 is insufficient, the vane 48 and the rolling piston 47 may separate near bottom dead center, disengaging the suction chamber 41a from the compression chamber 41b, and reducing the efficiency of the compressor 100. Therefore, as shown in FIG. 25 , a groove 43a extending the vane spring hole 43 is formed in the cylinder 40 from the vane spring hole 43 toward the cylinder chamber 41. The vane spring 49 is slidably fitted within the groove 43a. The groove 43a allows the vane spring 49 to move, ensuring the pressing force of the vane spring 49 at bottom dead center. The formation of the groove 43a in the vane spring hole 43 is not limited to the configuration of the second embodiment, and can also be applied to the first or third embodiments.

In addition, in the case of a single rotary compressor with one cylinder 40, it is desirable that the vane 48 be sized so that it does not protrude outward from the outer circumferential surface of the cylinder 40 when the orbital phase of the rolling piston 47 is 180° from the top dead center to the bottom dead center. This is because, although the overall length of the vane 48 is limited, if the vane 48 always protrudes from the outer circumferential surface of the cylinder 40, it would be difficult to attach the compression mechanism 4 to the sealed container 1.

On the other hand, in the case of a twin rotary compressor with two cylinders 40, as shown in Figure 23, when the top dead center phase is 0° and the orbital phase of the rolling piston 47 is 90° (or 270°), it is desirable that the dimensions of the vanes 48 be such that the back side does not protrude outward from the outer circumferential surface of the cylinder 40. In a twin rotary compressor, the orbital phases of the rolling pistons 47 provided in each cylinder 40 rotate with a 180° difference. In other words, with the above configuration, it is possible to prevent the back side of either vane 48 of the two cylinders 40 from always protruding outward from the outer circumferential surface of the cylinder 40.

Embodiment 3.
Next, a compressor 100 according to a third embodiment will be described with reference to Figures 26 to 28. Figure 26 is a longitudinal cross-sectional view schematically illustrating the cylinder 40 of the compressor 100 according to the third embodiment, with the vane 48 positioned at the top dead center phase. Figure 27 is a top view schematically illustrating the vane 48 of the compressor 100 according to the third embodiment. Figure 28 is a cross-sectional view taken along the line CC shown in Figure 27. Note that the same components as those of the compressor 100 described in the first and second embodiments are designated by the same reference numerals, and descriptions thereof will be omitted where appropriate.

26, the vane groove 42 does not penetrate all the way to the outer circumferential surface of the cylinder 40 on one end face side A of the two opposing end faces of the cylinder 40, and a first stop portion 42c for the vane 48 is formed at the end on the outer circumferential surface side of the cylinder 40. Furthermore, the vane groove 42 does not penetrate all the way to the outer circumferential surface of the cylinder 40 on the other end face side B of the cylinder 40, and a second stop portion 42d for the vane 48 is formed at the end on the outer circumferential surface side of the cylinder 40. In other words, the vane groove 42 has stop portions 42c and 42d formed on one end face side A and the other end face side B of the cylinder 40. The vane spring storage hole 43 has a perfectly circular cross-sectional shape perpendicular to the direction in which the vane spring storage hole 43 extends.

27 and 28, the vane 48 has a central portion 483 extending along the radial direction r of the cylinder 40, between a portion 481 located on one end face side A of the cylinder 40 where the first stop portion 42c is formed, and a portion 482 located on the other end face side B where the second stop portion 42d is formed. The length Lc of the central portion 483 along the radial direction r of the cylinder 40 is longer than the length La along the radial direction r of the portion 481 located on one end face side A of the cylinder 40 and the length Lb along the radial direction r of the portion 482 located on the other end face side B of the cylinder 40. The vane 48 is formed so that the length La of the portion 481 located on one end face side A of the cylinder 40 and the length Lb of the portion 482 located on the other end face side B of the cylinder 40 are approximately equal. As shown in FIG. 26 , the central portion 483 is configured to fit inside the vane spring 49, and when the rolling piston 47 is positioned at the top dead center phase, the back surface of the central portion 483 is located closer to the outer circumferential surface of the cylinder 40 than the end turn 49 a of the vane spring 49.

In the compressor 100 according to the third embodiment, the length La of the portion 481 of the vane 48 located on one end face side A of the cylinder 40 and the length Lb of the portion 482 located on the other end face side B are approximately equal, thereby stabilizing the vertical balance of the vane 48 during reciprocating motion. Furthermore, the vane groove 42 is provided with two stop portions 42c and 42d. Therefore, the vertical balance of the vane 48 can be stabilized even when the vane 48 contacts the stop portions 42c and 42d. Furthermore, the vane 48 has a central portion 483, which increases the lateral area of the vane 48, thereby enabling it to adequately support the load of the refrigerant differential pressure acting from the compression chamber 41b (high pressure) to the suction chamber 41a (low pressure).

In addition, in the compressor 100 according to this embodiment 3, an introduction groove 48a for introducing high-pressure gas refrigerant may be formed on either or both of the end face of portion 481 located on one end face side A of the cylinder 40 and the end face of portion 482 located on the other end face side B, as shown in Figures 16 and 17, for example.

Also, as shown in FIG. 18, for example, the entire back surface of the vane 48 may be rounded 48b at a portion 481 located on one end surface side A of the cylinder 40 where the first stop portion 42c is formed. Also, the entire back surface of the vane 48 may be rounded 48b at a portion 482 located on the other end surface side B of the cylinder 40 where the second stop portion 42d is formed. Also, as shown in FIG. 19, for example, the vane 48 may be rounded 48b only at the corners of the back surface of the vane 48 located on one end surface side A of the cylinder 40 where the first stop portion 42c is formed. Also, the vane 48 may be rounded 48b only at the corners of the back surface of the vane 48 located on the other end surface side B of the cylinder 40 where the second stop portion 42d is formed.

The compressor 100 and refrigeration cycle device 200 have been described above based on an embodiment, but are not limited to the configuration of the above-described embodiment. For example, the compressor 100 and refrigeration cycle device 200 are not limited to the configuration shown in the illustrations, and may include other components. In short, the compressor 100 and refrigeration cycle device 200 include the range of design modifications and application variations that would normally be made by a person skilled in the art, provided that they do not deviate from the technical concept.

1 Sealed container, 2 Motor section, 3 Rotating shaft, 4 Compression mechanism section, 5 Screw, 10 Upper container, 10a Through hole, 10b Recessed section, 11 Lower container, 12 Refrigerant suction pipe, 13 Refrigerant discharge pipe, 14 Refrigerating machine oil, 15 Closure part, 20 Stator, 21 Rotor, 30 Main shaft section, 31 Countershaft section, 32 Eccentric shaft section, 40 Cylinder, 40a Suction port, 41 Cylinder chamber, 41a Suction chamber, 41b Compression chamber, 42 Vane groove, 42a Stop portion, 42b Opening, 42c First stop portion, 42d Second stop portion, 43 Vane spring storage hole, 43a Groove portion, 44 Upper bearing, 44a Discharge port, 45 Lower bearing, 46 Discharge muffler, 47 Rolling piston, 48 Vane, 48a Introduction groove, 48b R-shape, 49 vane spring, 49a end winding, 100 compressor, 101 suction muffler, 102 flow path switching device, 103 outdoor heat exchanger, 104 expansion mechanism, 105 indoor heat exchanger, 106 refrigerant piping, 107 refrigeration circuit, 200 refrigeration cycle device, 420a projected location of stop portion, 481 portion of vane located on one end face side of cylinder, 482 portion of vane located on the other end face side of cylinder, 483 central portion, A one end face side, B other end face side, r radial direction.

Claims (14)

a sealed container forming an outer shell;
an electric motor section having a stator and a rotor;
a rotating shaft connected to the rotor and transmitting a driving force of the electric motor unit;
a compression mechanism unit connected to the rotary shaft and compressing the refrigerant by a driving force transmitted from the rotary shaft,
the rotating shaft has an eccentric shaft portion,
The compression mechanism portion includes:
a cylinder fixed to the sealed container and having a cylinder chamber into which a refrigerant is drawn and compressed;
a rolling piston that is fitted to the eccentric shaft portion and housed in the cylinder chamber, and rotates together with the eccentric shaft portion to compress the refrigerant;
a vane provided in a vane groove formed in a radial direction of the cylinder, the vane following the rolling piston to separate the cylinder chamber into a suction chamber and a compression chamber for the refrigerant;
a recessed portion in which the vane can slide is formed on an inner wall surface of the sealed container,
the vane groove is formed at one end face side of the two opposing end faces of the cylinder so as not to penetrate to the outer circumferential surface of the cylinder, and a stop portion for the vane is formed at an end portion on the outer circumferential surface side of the cylinder, and is formed at the other end face side of the cylinder so as to penetrate the outer circumferential surface of the cylinder,
the vane is configured such that a length along the radial direction of a portion located on the one end face side of the cylinder is longer than a length along the radial direction of a portion located on the other end face side of the cylinder , and when the rolling piston is positioned in a phase of top dead center, the portion located on the other end face side of the cylinder protrudes from the outer peripheral surface of the cylinder into the recess . The compressor of claim 1, wherein the vane is sized so that when it follows the rolling piston, the portion located on the one end face of the cylinder does not contact the stop portion, and when it is spaced from the rolling piston and pressed against the stop portion, the portion located on the other end face of the cylinder does not protrude outward from the outer circumferential surface of the cylinder. When the overall length of the vane at the portion located on the other end face side of the cylinder is Lb and the eccentricity of the eccentric shaft portion that determines the orbit of the rolling piston is e,
2×e/Lb<0.5
3. The compressor according to claim 1, wherein the relationship is: The compressor according to any one of claims 1 to 3, wherein when the stop portion is projected onto the other end surface of the cylinder as viewed from the one end surface of the cylinder, the groove width of the vane groove from the projected point of the stop portion to the outer peripheral surface of the cylinder is greater than the groove width of the vane groove from the projected point of the stop portion to the inner peripheral surface of the cylinder. A compressor according to any one of claims 1 to 4, wherein the entire back surface of the vane at the portion located on the one end face side of the cylinder is rounded, or the corners of the back surface are rounded. The compressor according to any one of claims 1 to 5, wherein the recess is formed by a through hole formed in the sealed container at a position corresponding to the vane groove, and a closing part that closes the through hole from an outer peripheral surface side of the sealed container. 7. The compressor according to claim 1, wherein a phase of the vane at top dead center is 0° and a portion of the vane located on the other end face side of the cylinder has a length such that the portion does not protrude outward from an outer circumferential surface of the cylinder when the phase of the top dead center of the vane is 0° and the orbital phase of the rolling piston is 90° or 270° . a vane spring that presses the vane so that a tip end of the vane abuts against an outer peripheral surface of the rolling piston,
The compressor according to any one of claims 1 to 7 , wherein the cylinder is formed with a vane spring housing hole for housing the vane spring. The compressor according to claim 8 , wherein the vane spring accommodation hole is formed with a central axis offset from a center in a thickness direction of the cylinder toward the one end face of the cylinder. 10. The compressor according to claim 8, wherein the vane has a central portion extending along the radial direction of the cylinder between a portion located on the one end face side of the cylinder and a portion located on the other end face side. 11. The compressor according to claim 10, wherein the central portion is configured to fit inside the vane spring, and when the rolling piston is in a phase of top dead center, a back surface of the central portion is located closer to an outer peripheral surface of the cylinder than an end turn of the vane spring. The cylinder has a groove extending from an end of the vane spring storage hole toward the cylinder chamber,
The compressor according to any one of claims 8 to 11 , wherein the vane spring is slidably fitted inside the groove. The compressor according to any one of claims 1 to 12 , wherein the vane has an introduction groove formed along the radial direction to introduce the high-pressure gas refrigerant remaining in the sealed container. At least a compressor according to any one of claims 1 to 13 ;
an outdoor heat exchanger that exchanges heat between the refrigerant flowing therein and the outdoor air;
an indoor heat exchanger that exchanges heat between the refrigerant flowing therein and the indoor air;
a refrigeration cycle device having an expansion mechanism that expands refrigerant flowing into the outdoor heat exchanger or the indoor heat exchanger, and a refrigeration circuit connected to the expansion mechanism via a refrigerant pipe.