JPH0247600B2 - - Google Patents

Description

[Detailed Description of the Invention] [Field of Application of the Invention] The present invention relates to a compressor incorporated in a refrigeration device such as a refrigerator or an air conditioner, and particularly relates to a compressor that is incorporated in a refrigeration device such as a refrigerator or an air conditioner, and particularly relates to a compressor that is incorporated in a refrigeration device such as a refrigerator or an air conditioner. The present invention relates to a compressor that is oriented toward

[Background of the invention]

First, a conventional compressor (Utility Model Application Publication No. 55-60489) will be explained.

FIG. 3 is a longitudinal sectional view showing an example of a horizontal compressor as a conventional compressor.

In FIG. 3, a case 1 also serves as an oil reservoir, and an electric motor 22 and a compression element 23 are housed in the case 1.

The electric motor 22 includes a stator 19 and a rotor 20.
A shaft 4 having a crank 3 and having a hollow shaft hole 17 at one end thereof is fitted into the rotor 20.

The compression element 23 includes a cylinder 2, a spring 9 inserted into a spring hole 30 bored at the lower end of the cylinder 2, the shaft 4, a bearing for the shaft 4, and a side wall of the cylinder 2, A side plate A5, a side plate B6, a bolt 21 that fastens the side plate A5, side plate B6, and the cylinder 2, a roller 7 that is fitted in the crank 3 and rotates eccentrically along the inside of the cylinder 2, A vane 1 reciprocates within a groove 8 of a cylinder 2 while its tip abuts and the other end is pushed by a spring 9.
0. It consists of a pump chamber 12 surrounded by the back surface 11 of the vane 10, the groove 8 of the cylinder 2, and the side plates A5 and B6. The side plate A5 has a straight suction port 14 that can suck the lubricating oil 13 inside the case 1 into the pump chamber 12.
The side plate B6 has a straight discharge port 16 that can discharge lubricating oil 13 from the pump chamber 12 to an oil feed pipe 15 related to an oil feed path, and the oil feed pipe 15 discharges lubricant oil 13 to a shaft hole 17 related to one end of the shaft. Furthermore, oil can be supplied from the shaft hole 17 to the required lubricating parts through the branch hole 18.

In this configuration, when the compressor is operated and the shaft 4 rotates, the roller 7 rotates accordingly, the vane 10 is pushed by the spring 9, and the vane 10 is moved around the cylinder 2 with its tip in contact with the roller 7. It reciprocates within the groove 8, compresses the refrigerant that has flowed in from the refrigerant suction port (not shown), and discharges it from the refrigerant discharge port (not shown).

On the other hand, when the vane 10 reciprocates, the pump chamber 1
The volume of 2 changes and performs a pumping action. That is, when the volume of the pump chamber 12 increases, the lubricating oil 13 is sucked in from the suction port 14, and the pump chamber 12
When the volume of the lubricating oil 13 becomes smaller, the lubricating oil 13 is discharged from the discharge port 16 to the oil pipe 15. The lubricating oil 13 sent to the oil pipe 15 is supplied to required lubricating parts through the shaft hole 17 and branch hole 18.

By the way, the above-mentioned conventional technology has the following problems.

That is, when the volume of the pump chamber 12 increases, the lubricating oil 13 in the case 1 is sucked in from the suction port 14, but at the same time, the lubricating oil 13 in the oil feed pipe 15 is sucked in.
Since oil is also sucked into the pump chamber 12, the oil supply pipe 15
The lubricating oil 13 inside flows backward. In addition, the pump chamber 12
When the internal volume becomes smaller, the lubricating oil 13 is discharged from the discharge port 16 into the oil feed pipe 15, but at the same time, the lubricating oil 13 is also discharged from the suction port 14 into the case 1.
, the lubricating oil 13 also flows back in this case.

In particular, since the discharge port 16 side requires the resistance of the oil feed pipe 15 and the head of the lubricating oil 13 up to the axis, the resistance on the discharge port 16 side is large, and the lubricating oil 13 tends to flow back toward the suction port 14 side. The lubricating oil 13 may not reach the axial center of the shaft 4.

In order to prevent this and obtain a sufficient amount of oil supply to the shaft hole 17, the diameter of the suction port 14 should be made small.
It was necessary to make it difficult for the lubricating oil 13 to flow back toward the suction port 14 by increasing the backflow resistance.

However, if the backflow resistance of the suction port 14 is large, the forward flow resistance also becomes large.
During the suction stroke in which the pump rotates and the volume of the pump chamber 12 increases, the pressure within the pump chamber 12 drops rapidly, and the refrigerant dissolved in the sucked lubricating oil 13 begins to dissolve, generating bubbles. Then, in a discharge stroke in which the volume of the pump chamber 12 decreases with air bubbles mixed in the lubricant oil 13, the lubricant oil 13 is sent from the discharge port 16 to a required lubricating part. If the lubricating oil 13 containing air bubbles is supplied to lubricating parts such as bearings in this way, the generation of oil pressure will be hindered and an oil film will not be formed, resulting in problems that need to be improved, such as seizing. Ta.

The above problems are remarkable in the case of a variable rotation speed compressor. In other words, the flow rate entering and exiting the pump chamber during low-speed rotation decreases, so in order to obtain the necessary head and oil supply amount during the discharge stroke, the flow path cross-sectional area of the suction port must be reduced and the flow velocity here increased. backflow resistance must be increased. However, during high-speed rotation, the flow rate in and out of the pump chamber increases, so if the cross-sectional area of the suction port is made small, the forward flow resistance will also be large, and the pressure drop in the pump chamber during the suction stroke will increase, causing air bubbles. It is more likely to occur.

[Object of the Invention] The present invention has been made to solve the problems of the prior art described above, and it increases the resistance during backflow in the pump suction stroke, while ensuring the lift head and oil supply amount at low speeds, while maintaining high speeds. The purpose is to provide a compressor that can reduce the increase in resistance during forward flow of lubricating oil, prevent the generation of bubbles from lubricating oil, and supply a sufficient amount of lubricant to the required lubricated parts. It is something.

[Configuration of the Invention] The configuration of the compressor according to the present invention includes, in a case that also serves as an oil reservoir, an electric motor, a cylinder, a shaft having a crank, and a roller that is fitted into the crank and rotates eccentrically along the inside of the cylinder. , a vane that reciprocates in a groove of the cylinder while abutting the roller, a side plate that serves as a bearing of the shaft and a side wall of the cylinder and has a suction port and a discharge port, and a groove between the back surface of the vane and the cylinder. and a compression element having a pump chamber surrounded by the side plate, and the compressor element has a compression element having a pump chamber surrounded by the side plate. In a compressor configured to pressurize lubricating oil flowing into the pump chamber through the suction port and forcefully send it from the discharge port to one end of the shaft via the oil feed path, to at least one port,
A fluid valve is provided in which a plurality of fluid diodes are connected in series, and at least one of the plurality of fluid diodes has a tapered nozzle shape with a large diameter portion on the suction side and a small diameter portion on the discharge side. This is a fluid diode.

That is, the compressor of the present invention includes a plurality of fluid diodes in either or both of the suction port that guides the lubricating oil in the case to the pump chamber or the discharge port that sends the lubricating oil in the pump chamber to the oil supply path. This is a port with a fluid valve in which fluid valves connected in series are arranged, and the difference between the resistance in the backward flow direction and the resistance in the forward flow direction at each port is increased.

[Operation of the Invention] The operation of a fuel pump provided with a fluid valve having a plurality of fluid diodes connected in series as described above will be described.

During the discharge stroke, where the volume inside the pump chamber becomes smaller, by using a suction port with a fluid valve that has multiple fluid diodes connected in series, backflow resistance is increased, the necessary head is obtained, and refueling is possible with less backflow. In the suction stroke in which the internal volume of the pump chamber increases, the forward flow resistance of the suction port with the fluid valve can be reduced and the generation of bubbles from the lubricating oil can be prevented.

Furthermore, when used in a variable rotation speed compressor, in order to obtain the necessary head and oil supply amount at low rotation speeds,
If a single fluid diode is used in a fluid valve, the cross-sectional area of the flow path must be reduced and the flow velocity must be increased in order to obtain sufficient backflow resistance during the discharge stroke, whereas multiple fluid diodes are used. For example, the backflow resistance can be increased without reducing the cross-sectional area of the flow path, and the necessary head and oil supply amount can be secured.

On the other hand, if a single fluid diode is used in the suction stroke during high-speed rotation, the forward flow resistance will be large because the cross-sectional area of the flow path is small, and the pressure drop in the pump chamber will be large. If a diode is used, the cross-sectional area of the flow path is large, so the pressure drop in the pump chamber is small, and the generation of bubbles can be prevented.

[Embodiments of the invention] Examples will be explained below.

FIG. 1 is a longitudinal sectional view showing a compressor according to a first embodiment of the present invention, and FIG. 2 is an enlarged longitudinal sectional view showing details of the vicinity of the pump chamber in FIG. 1.

This compressor is a horizontal compressor, and the same parts as in FIG. 3 are denoted by the same numbers.

The compressor of this embodiment shown in FIG. 1 includes an electric motor 22 and a cylinder 2 in a case 1 that also serves as an oil reservoir.
A, shaft 4 with crank 3, crank 3
a roller 7 that is fitted in and rotates eccentrically along the inside of the cylinder 2A; a vane 10 that reciprocates within the groove 8 of the cylinder 2A while contacting the roller 7;
They are arranged on both sides of the cylinder 2A, and serve as both the bearing of the shaft 4 and the side wall of the cylinder 2A, and have a suction port 32 (details will be described later) for the lubricating oil 13 on one side, and a discharge port 34 (described in detail later) with a fluid valve on the other side. Side plate A5A and side plate B6, each having a side plate (details described later)
A, a side plate cover 24 fixed to the side surface of this side plate B6A and having a hole 25 in the center that opens to the shaft hole 17 of the shaft 4; and the discharge port 3 with a fluid valve.
4 and the hole 25 of the side plate cover 24, and the lubricating oil 1 is discharged from the discharge port 34 with a fluid valve.
3 to the shaft hole 17
3. Rear surface 11 of vane 10 and groove 8 of cylinder 2A
and a compression element 23A having a pump chamber 12 surrounded by a side plate A5A, a side plate B6A, and a sealing part 31 provided at the lower end of the spring hole 30.

The suction port 32 with a fluid valve and the discharge port 34 with a fluid valve will be explained in more detail using FIG. 2. The suction port 32 with a fluid valve includes a first nozzle-shaped suction fluid diode 40 having a tapered circular cross section and a small diameter portion 53 , a tapered portion 54 , and a large diameter portion 55 .
The large diameter portion 55 of the first nozzle-type suction fluid diode 40 opens into the case 1. The small diameter portion 50 of the second nozzle type suction fluid diode 41 is located in a space A35 communicating with the pump chamber 12.
It is arranged so that it opens at the. On the other hand, the discharge port 34 with a fluid valve has a small diameter portion 47,
A first nozzle-shaped discharge fluid diode 42 having a tapered circular cross section and a tapered portion 48 and a large diameter portion 49.
and a second nozzle-type discharge fluid diode 43 having a tapered circular cross section and having a small diameter portion 44, a tapered portion 45, and a large diameter portion 46 in the same direction. diode 4
The second large diameter portion 49 opens toward the pump chamber 12 side, and the second nozzle type discharge fluid diode 43 has a small diameter portion 4 .
4 is arranged so as to open into a space B37 communicating with the oil feed path 33.

In this embodiment, at least one of the two nozzle-type fluidic diodes combined may be manufactured as a separate component. In the example shown in FIG. 2, the first nozzle-type suction fluid diode 40 and the first nozzle-type discharge fluid diode 42 are manufactured separately by press molding or the like, and are attached to the suction and discharge ports respectively for processing and assembly. is facilitated.

The operation of the compressor configured in this way will be explained.
When the compressor is operated and the shaft 4 rotates, the roller 7 rotates and the vane 10 rotates.
Pushed by the spring 9, the cylinder 2A reciprocates within the groove 8 of the cylinder 2A while its tip abuts against the roller 7, compressing the refrigerant.

On the other hand, during the suction stroke of the pump in which the volume inside the pump chamber 12 is about to increase due to the reciprocating motion of the vane 10, the fluid flows from the first nozzle-type suction fluid diode 40 to the second nozzle-type suction fluid diode 41 to the case 1. The lubricating oil 13 inside is sucked. At this time, the lubricating oil 13 is also sucked in from the fluid valve-equipped discharge port 34 side, but the flow of the lubricating oil 13, which is expanded in the space B37 connected to the second nozzle type discharge fluid diode 43, is Small diameter portion 44 of two-nozzle discharge fluid diode 43
The flow constricts at this point, creating a large flow resistance, the so-called edge effect, which makes backflow difficult. Further, the flow gradually expanded in the tapered portion 45 of the second nozzle-type discharge fluid diode 43 contracts again in the small diameter portion 47 of the first nozzle-type discharge fluid diode 42, and a large flow resistance is generated here again.
Therefore, the space B3 communicating with the oil supply path 33
The flow resistance from 7 to the pump chamber 12 is large, making it difficult for the lubricating oil 13 to flow back. In this way, most of the lubricating oil 13 is sucked in from the fluid valve-equipped suction port 32 side.

In the pump discharge stroke in which the vane 10 descends and the volume inside the pump chamber 12 becomes smaller, lubricating oil 13 flows from the fluid valve-equipped discharge port 34 side to the oil supply path 33.
Discharge. At this time, lubricating oil 13 is also discharged from the suction port 32 side with a fluid valve, but the lubrication oil 13 is expanded in a space A35 that communicates with the pump chamber 12 and is connected to the second nozzle type suction fluid diode 41. The flow of the oil 13 contracts in the small diameter portion 50, creating a large flow resistance there and making it difficult to flow back. Furthermore, the flow that has been gradually expanded in the tapered portion 51 of the second nozzle-type suction fluid diode 41 contracts again in the small diameter portion 53 of the first nozzle-type suction fluid diode 40, and a large flow resistance is generated here again. . Therefore, the flow resistance of the backflow from the space A35 communicating with the pump chamber 12 to the case 1 is large, and the lubricating oil 13 becomes difficult to flow back.
In this way, most of the lubricating oil 13 is discharged from the fluid valve-equipped discharge port 34 side.

By the way, the flow resistance when attempting to flow from the inside of the pump chamber 12 into the case 1 through the suction port 32 with a fluid valve is
A first nozzle-type suction fluid diode 4 constituting 2
This is represented by the diameter of the small diameter portion of the zero and second nozzle type suction fluid diodes 41, and the smaller the diameter of the small diameter portion, the greater the flow resistance. On the other hand, when the lubricating oil 13 flows backward from the shaft hole 17 of the shaft 4 into the pump chamber 12, the flow resistance is caused by the first nozzle-type discharge fluid diode 42 and the second nozzle-type discharge fluid that constitute the fluid valve-equipped discharge port 34. Not only the diameter of the small diameter portion of the diode 43 but also the flow path resistance in the oil feed path 33 and the head of the lubricating oil 13 from the discharge port 34 with a fluid valve to the shaft hole 17 of the shaft 4 are added. Therefore, if a fluid valve formed by connecting two nozzle-shaped fluid diodes is provided to the discharge port as in this embodiment, compared to the conventional example in which the discharge port is a straight hole, Flow resistance from the pump chamber 12 to the oil feed path 33 is small. Accordingly, the resistance on the side of the suction port 32 with a fluid valve required to overcome the resistance on the side of the discharge port 34 with a fluid valve and supply the lubricating oil 13 to the shaft hole 17 becomes smaller. For this reason, suction port 3 with fluid valve
The diameter of the small diameter portion of the nozzle-type suction fluid diode constituting 2 can be increased. In addition, if the suction port 32 with a fluid valve is configured with two stages of nozzle-type fluid diodes in series as in this embodiment,
Further, since the backflow resistance increases, the diameter of the small diameter portion of the nozzle-type fluidic diode can be made even larger.

According to the embodiment described above, a fluid valve formed by connecting nozzle-shaped fluid diodes with a tapered circular cross section in two stages is disposed at the suction port and the discharge port, so that the suction port 32 with a fluid valve is configured. Even if the diameter of the small diameter part of the nozzle-type suction fluid diode is increased, a sufficient amount of lubricant can be obtained.
Since the flow resistance when suctioning into the pump chamber 12 can be reduced, the drop in pressure within the pump chamber 12 during the pump suction stroke in which the volume of the pump chamber 12 increases is reduced, and the influence of negative pressure generated within the pump chamber at this time is reduced. This has the effect of preventing the risk of the refrigerant dissolved in the lubricating oil 13 melting out, forming bubbles, and mixing into the oil.

Moreover, since the discharge port 34 with a fluid valve is also composed of two stages of nozzle-type discharge fluid diodes in series, the flow resistance from the oil feed path 33 to the pump chamber 12 can be increased, so that the suction port 32 side with a fluid valve can be increased. Even if the diameter of the small diameter portion of the nozzle-type suction fluid diode is increased, the amount of backflow from the discharge port 34 side with a fluid valve is small, and sufficient oil supply can be ensured.

Furthermore, in this embodiment, one of the two nozzle-shaped fluid diodes is manufactured as a separate part, so it is easy to process by press molding etc., and the tip edge can be formed sharply, so the fluid valve On the contrary, it has the effect of increasing the forward flow resistance ratio.

In addition, in this embodiment, the suction port 3 with a fluid valve
2. The discharge port 34 with a fluid valve has been described in which two stages of nozzle-shaped fluid diodes are arranged, but this may be further configured with multiple stages of nozzle-shaped fluid diodes, thereby achieving the above-mentioned effects. can be made even larger. Also,
Either the suction port or the discharge port is a port with a fluid valve equipped with a fluid valve formed by connecting multiple (two-stage or multi-stage) nozzle-type fluid diodes in series, and the other is the same straight port as before. Depending on the model, a sufficient amount of lubricating oil without air bubbles can be supplied to the required lubricating parts even if the port is used.

Next, another embodiment will be described.

FIG. 4 is a longitudinal cross-sectional view showing a compressor according to a second embodiment of the present invention, FIG. 5 is an enlarged cross-sectional view showing details of the vicinity of the pump chamber in FIG. 4, and FIG. FIG. 7 is a cross-sectional view taken in the direction of the arrow in FIG. 5 (with the side plate cover removed).

This compressor is also a horizontal compressor, and the same parts as in FIG. 1 are denoted by the same numbers.

The compressor of this embodiment shown in FIG. 4 has a motor 22 in a case 1 which also serves as an oil reservoir, and components other than the side plate A5B and side plate B6B (details will be described later) are the same as the compressor shown in FIG. It has exactly the same compression element 23B.

The side plate B6B is made of a material that is easily molded, such as sintered metal, and is disposed on one side of the cylinder 2A. This side plate B6B has a nozzle-shaped discharge fluid diode 2 with a tapered circular cross section.
8 and a spiral discharge fluid diode 29 connected in series to the small diameter portion 58 side of the nozzle-shaped discharge fluid diode 28 and having a spiral chamber 60 and a communication hole 61 bored in contact with the inner wall surface of the spiral chamber 60. A discharge port 39 with a fluid valve is provided so that the nozzle-shaped discharge fluid diode 28 is located on the suction side (pump chamber 12 side). A side plate A5B disposed on the other side of the cylinder 2A includes a nozzle-shaped suction fluid diode 26 with a tapered circular cross section;
The small diameter portion 6 of this nozzle-type suction fluid diode 26
The nozzle-shaped suction fluid diode 26 connects the spiral suction fluid diode 27, which has a spiral chamber 67 and a communication hole 68 formed so as to be in contact with the inner wall surface of the spiral chamber 67, connected in series on the 6 side. )
A suction port 38 with a fluid valve arranged so as to
is provided.

The suction port 38 with a fluid valve and the discharge port 39 with a fluid valve will be explained in more detail using FIGS. 5 to 7. Suction port 38 with fluid valve
A cylindrical spiral chamber 67 is bored in the lower part of the side plate A5B so as to open downward into the case 1, and a communication hole 68 is connected to the pump chamber 12 so as to be in contact with the inner wall surface of the spiral chamber 67. Further, a suction piece 63 manufactured by press molding or the like having a small diameter part 66, a tapered part 64, and a large diameter part 65 and forming a tapered nozzle-shaped suction fluid diode 26 is attached to the small diameter part. 66 is press-fitted into the swirl chamber 67 so as to open into the swirl chamber 67.
7 into the case 1 is closed, and a spiral suction fluid diode 27 is formed above the nozzle fluid diode 26.

On the other hand, the discharge port 39 with a fluid valve is connected to the side plate B6.
A cylindrical spiral chamber 60 on the side of B, and this spiral chamber 6
A communication hole 61 communicating with an oil feed port 62 connected to the oil feed path 33 is formed so as to be in contact with the inner wall surface of the oil feed passage 33, and the communication hole 61 is sealed with a side plate cover 24, thereby forming a spiral discharge fluid diode 29. was formed. In addition, a small diameter portion 5 is provided in the swirl chamber 60.
8 is open, and a nozzle-shaped discharge fluid diode 28 having a tapered portion 57 is formed so that a large diameter portion 59 communicates with the pump chamber 12.

Here, in the example shown in FIG. 5, the small diameter portion 66 on the tip side of the nozzle-shaped suction fluid diode 26 is made to protrude into the spiral chamber 67 of the spiral-shaped suction fluid diode 27,
The small diameter portion 58 on the tip side of the nozzle-shaped discharge fluid diode 28 is connected to the spiral chamber 6 of the spiral-shaped discharge fluid diode 29.
It is configured to protrude to 0.

The operation of the compressor configured in this way will be explained.
In this embodiment as well, as in the first embodiment shown in FIG. 1, when the shaft 4 rotates, the vanes 10 reciprocate accordingly.

Due to this reciprocating movement of the vane 10, the lubricating oil 13 in the case 1 is sucked from the nozzle-shaped suction fluid diode 26 during the pump suction stroke in which the volume in the pump chamber 12 is about to increase. This lubricant 1
3 is sent to the spiral suction fluid diode 27 with low resistance, and from there passes through the communication hole 68 to the pump chamber 12.
sent to with less resistance. At this time, lubricating oil 13 is also sucked in from the fluid valve-equipped discharge port 39 side, but the oil supply path 3 of the spiral discharge fluid diode 29
The lubricating oil 13 flows in from the communication hole 61 communicating with the volute chamber 60 so as to be in contact with the inner wall of the volute chamber 60, a swirling flow is generated inside the vortex chamber 60, and the lubricating oil 13 flows out from the small diameter portion 58 of the nozzle-shaped discharge fluid diode 28 that opens into the vortex chamber 60. It becomes difficult. Furthermore, a contraction occurs in the flow at the end face of this small diameter portion 58, and a large flow resistance occurs here. Since the discharge port 39 with a fluid valve is configured with two stages of discharge fluid diodes, the resistance in the reverse flow direction is large, and most of the lubricating oil 13 is sucked in from the suction port 38 side with a fluid valve.

On the other hand, in the pump discharge process in which the vane 10 is lowered and the volume inside the pump chamber 12 is reduced, the oil supply path 3 is moved from the fluid valve-equipped discharge port 39 side with less resistance.
The lubricating oil 13 is discharged to 3. At this time, the lubricating oil 13 is also discharged from the suction port 38 side with a fluid valve. In this case, the lubricating oil 13 flows from the communication hole 68 communicating with the pump chamber 12 so as to be in contact with the inner wall of the spiral chamber 67 of the spiral suction fluid diode 27, causing a swirling flow therein and increasing the resistance. The small diameter portion 66 of the nozzle-shaped suction fluid diode 26 that opens into the chamber 67 is less likely to flow out. Furthermore, a contraction occurs in the flow at the end of this small diameter portion 66, resulting in even greater flow resistance. Therefore,
As in this embodiment, the suction port 38 with a fluid valve is
By constructing a stage of suction fluid diodes,
flow backwards. The resistance is large, and most of the lubricating oil 13 is discharged to the fluid valve-equipped discharge port 39 side.

Incidentally, the magnitude of flow resistance of both the suction port 38 with a fluid valve and the discharge port 39 with a fluid valve is represented by the small diameter portions 58 and 66, respectively. In this example, since a two-stage fluidic diode is used, the resistance in the reverse flow direction can be increased compared to the conventional example in which the suction port and the discharge port are straight holes. Even if the diameter is increased, a sufficient amount of oil can be obtained. If the diameter of the small diameter portion 66 is increased, the resistance during suction at the suction port 38 with a fluid valve will be reduced, and the pressure drop in the pump chamber 12 will be reduced when the volume of the pump chamber 12 increases. Under the influence of the negative pressure at this time, the refrigerant dissolved in the lubricating oil 13 will not dissolve and air bubbles will not be mixed into the oil.

According to this embodiment described above, a fluid valve is provided in which the spiral fluid diodes and the nozzle fluid diodes of the suction port and the discharge port are combined in two stages. Compared to the embodiment shown in FIG. 1 in which stages are combined, the resistance to reverse flow in the forward direction can be increased. Therefore, a larger amount of oil can be supplied, and the diameter of the small diameter part of the fluid diode is increased to reduce suction resistance and to ensure that there is no risk of air bubbles entering the lubricating oil 13 due to the influence of negative pressure during the pump suction stroke. This has the effect of being able to prevent this. That is, according to this embodiment, the reverse and forward flow resistance ratios are increased, and the increase in resistance at high speeds can be reduced while ensuring the amount of oil supplied at low speeds.

Furthermore, since the tip of the nozzle fluid diode is structured to protrude into the spiral chamber of the spiral fluid diode, the flows within the spiral chamber interfere with each other during backflow, resulting in greater resistance, thereby further enhancing the above effect.

In all of the above embodiments, one side plate A is provided with a suction port with a fluid valve, and the other side plate B is provided with a discharge port with a fluid valve. Both ports may be provided. This embodiment will be explained next.

FIG. 8 is a vertical cross-sectional view of a main part showing a compressor according to a third embodiment of the present invention, FIG. 9 is a cross-sectional view taken along the - arrow in FIG. 8, and FIG. The sectional view, FIG. 11, is a view as seen from the arrows in FIG. 8 (with the cover removed).

In the figures, the same parts are denoted by the same numbers as in FIGS. 4 to 7. In this embodiment, a suction port 38 with a fluid valve is provided with a fluid valve formed by connecting a nozzle type suction fluid diode 26 and a spiral type suction fluid diode 27 in series on one side plate B6C.
and a discharge port 39 with a fluid valve provided with a fluid valve formed by connecting a nozzle-type discharge fluid diode 28 and a spiral-shaped discharge fluid diode 29 in series, and no port is provided on the other side plate A5C. This is what I did.

The compressor constructed in this manner also operates in the same manner as the compressor shown in FIG. 4 and provides the same effects. Furthermore, since the suction port and the discharge port are provided only on one side plate B6C, there is an advantage that the number of man-hours for processing and assembling the compressor is reduced compared to the compressor according to FIG. 4.

Finally, another embodiment will be described.

In this embodiment, the present invention is applied to a vertical compressor.

FIG. 12 is a sectional view of essential parts showing a compressor according to a fourth embodiment of the present invention, FIG. 13 is a sectional view taken along the - arrow in FIG. 12, and FIG. 14 is a - arrow sectional view in FIG.
15 is a sectional view taken along the - arrow in FIG. 12.

This embodiment also has a suction port 38 with a fluid valve and a discharge port 39 with a fluid valve on one side plate B6C, and the other side plate A5C, like the compressor (horizontal compressor) according to FIG. It is designed so that no ports are provided.

The compressor constructed in this manner also operates in the same manner as the compressor shown in FIG. 4 and provides the same effects.

〔Effect of the invention〕

As described in detail above, according to the present invention, it is possible to provide a compressor that can supply a sufficient amount of lubricating oil without air bubbles to required lubricating parts.

Further, it is possible to provide a variable rotation speed compressor that can secure the required lift and oil supply amount during low speed rotation, and supply bubble-free lubricating oil during high speed rotation.

[Brief explanation of drawings]

FIG. 1 is a longitudinal sectional view showing a compressor according to a first embodiment of the present invention, FIG. 2 is an enlarged longitudinal sectional view showing details of the vicinity of the pump chamber in FIG. 1, and FIG.
FIG. 4 is a vertical cross-sectional view showing an example of a horizontal compressor as a conventional compressor. FIG. 4 is a vertical cross-sectional view showing a compressor according to a second embodiment of the present invention. FIG. FIG. 6 is an enlarged cross-sectional view showing details of the vicinity of the chamber, FIG.
View from the arrow in the figure (with the cover removed),
FIG. 8 is a vertical cross-sectional view of main parts showing a compressor according to a third embodiment of the present invention, FIG. 9 is a cross-sectional view taken along the - arrow in FIG. 8, and FIG. 10 is a - arrow cross-sectional view in FIG. 11 is a cross-sectional view in the direction of the arrows in FIG. 8 (with the cover removed), and FIG.
FIG. 1 is a longitudinal sectional view of main parts showing a compressor according to an embodiment of
3 is a cross-sectional view taken along the - arrow in FIG. 12, FIG. 14 is a cross-sectional view taken along the - arrow in FIG. 13, and FIG.
FIG. 12 is a sectional view taken along the - arrow in FIG. 12; 1...Case, 2A...Cylinder, 3...Crank,
4...Shaft, 5A, 5B, 5C...Side plate A, 6
A, 6B, 6C...Side plate B, 7...Roller, 8...Groove,
10... Vane, 11... Back, 12... Pump chamber, 1
3...Lubricating oil, 17...Shaft hole, 22...Electric motor, 23
A, 23B... Compression element, 26... Nozzle type suction fluid diode, 27... Spiral type suction fluid diode,
28... Nozzle type discharge fluid diode, 29... Spiral type discharge fluid diode, 32... Suction port with fluid valve, 33... Oil feed path, 34... Discharge port with fluid valve, 35... Space A, 37... Space B, 38
...Suction port with fluid valve, 39...Discharge port with fluid valve, 40...First nozzle type suction fluid diode, 41...Second nozzle type suction fluid diode, 4
2...First nozzle type discharge fluid diode, 43...Second nozzle type discharge fluid diode, 44...Small diameter portion,
46...Large diameter part, 47...Small diameter part, 49...Large diameter part, 5
0...Small diameter part, 52...Large diameter part, 53...Small diameter part, 55
...Large diameter part, 58...Small diameter part, 59...Large diameter part, 60...
Swirl chamber, 61...Communication hole, 65...Large diameter section, 66...Small diameter section, 67...Swirl chamber, 68...Communication hole.

Claims (1)

[Scope of Claims] 1. A shaft having an electric motor, a cylinder, and a crank is housed in a case that also serves as an oil reservoir; a roller that is fitted into the crank and rotates eccentrically along the inside of the cylinder; A vane that reciprocates in a groove of the cylinder, a side plate that serves as a bearing of the shaft and a side wall of the cylinder and has a suction port and a discharge port, and is surrounded by the back surface of the vane, the groove of the cylinder, and the side plate. a compression element having a pump chamber, and the suction port is moved from inside the case to the pump chamber by a pumping action caused by reciprocating movement of the vane as the shaft rotates driven by the electric motor. In a compressor configured to pressurize lubricating oil that has flowed into the shaft and forcefully send it from the discharge port to one end of the shaft via the oil supply path, a plurality of A fluid valve consisting of fluid diodes connected in series shall be installed,
A compressor characterized in that at least one of the plurality of fluid diodes is a tapered nozzle-shaped fluid diode having a large diameter portion on the suction side and a small diameter portion on the discharge side. 2 The plurality of fluid diodes are two nozzle-shaped fluid diodes with a tapered circular cross section combined in the same direction, with the large diameter part of the nozzle-shaped fluid diodes facing the suction side and the small diameter part facing the discharge side. 2. The compressor according to claim 1, wherein the compressor is arranged so as to face the nozzle-shaped fluid diode disposed on the discharge side to provide a space. 3. At least one of the nozzle-type fluid diodes combined in the same direction is equipped with a separate body, and the tip edge of the small diameter portion of the separate body is formed sharply. Compressor according to item 2. 4. A plurality of fluid diodes, a nozzle-shaped fluid diode with a tapered circular cross section, and a spiral chamber arranged on the small diameter side of the nozzle-shaped fluid diode;
a spiral fluid diode having a communication hole bored in contact with the inner wall surface, and the nozzle fluid diode is arranged on the suction side and the spiral fluid diode is arranged on the discharge side. A compressor according to claim 1, characterized in that the compressor is configured as follows. 5. The compressor according to claim 4, wherein the small diameter portion of the nozzle-shaped fluid diode projects into the spiral chamber of the spiral fluid diode.