JP7618061B2 - Oil supply parts, compressors, and refrigeration cycle devices - Google Patents

Description

The present disclosure relates to an oil supply part provided in a compressor to improve the ability to supply refrigeration oil to sliding parts at low rotation speeds, a compressor equipped with the oil supply part, and a refrigeration cycle device equipped with the compressor.

Conventionally, the rotating shaft of a compressor is formed with an oil supply hole that opens at one end. When the rotating shaft rotates, refrigeration oil, which is a lubricant, is sucked into the oil supply hole. The refrigeration oil sucked into the oil supply hole is then supplied to sliding parts such as the compression mechanism. In addition, a conventional compressor has been proposed in which an oil supply part is provided at the end of the rotating shaft on the side where the oil supply hole opens, thereby improving the supply capacity of refrigeration oil to the sliding parts when the rotating shaft is in the low rotation range (see Patent Document 1).

Specifically, Patent Document 1 discloses an oil supply part under the name of a suction member. The oil supply part described in Patent Document 1 has a flat main plate. A through hole is formed in the main plate. The main plate has a plurality of engagement claws protruding from a position on the outer periphery side of the main plate than the through hole. The plurality of engagement claws are inserted into the oil supply hole of the rotating shaft, and the outer surfaces of the plurality of engagement claws come into contact with the inner periphery of the rotating shaft, thereby fixing the oil supply part described in Patent Document 1 to the end of the rotating shaft on the side where the oil supply hole is open. In an oil supply part configured in this way, a through hole is formed on the inner periphery side of the plurality of engagement claws inserted into the oil supply hole. Therefore, the diameter of the through hole is smaller than the diameter of the oil supply hole of the rotating shaft. In this way, by configuring the oil supply part to suck refrigeration oil from a through hole smaller than the diameter of the oil supply hole of the rotating shaft into the oil supply hole of the rotating shaft, it is possible to improve the supply capacity of refrigeration oil to the sliding part when the rotating shaft is in a low rotation range.

Japanese Utility Model Application Publication No. 63-154787

In the lubrication part described in Patent Document 1, each of the engaging claws extends straight in the axial direction of the rotating shaft, in other words, in the direction in which the oil supply hole is formed. Therefore, in the lubrication part described in Patent Document 1, when the lubrication part is fixed to the rotating shaft, each of the engaging claws is inserted into the oil supply hole of the rotating shaft while most of the outer surface of each of the engaging claws is in contact with the inner peripheral surface of the rotating shaft. For this reason, the lubrication part described in Patent Document 1 has a problem in that it is difficult to attach to the rotating shaft of the compressor because there is a large resistance when each of the engaging claws is inserted into the oil supply hole of the rotating shaft.

The present disclosure has been made to solve the above-mentioned problems, and has as its first object to obtain an oil supply part that can be attached to a rotating shaft of a compressor more easily than before. The present disclosure has as its second object to obtain a compressor equipped with such an oil supply part. The present disclosure has as its third object to obtain a refrigeration cycle device equipped with such a compressor.

The oil supply part according to the present disclosure is an oil supply part provided in a compressor having an oil supply hole that opens into a first end, and a rotating shaft that supplies refrigeration oil sucked into the oil supply hole to a compression mechanism, the oil supply part comprising: a main plate portion having through holes formed therein; and a plurality of insertion parts that protrude from a position in the main plate portion that is closer to the outer periphery of the main plate portion than the through holes and are inserted into the oil supply hole, and each of the insertion parts has a second end that is one end, a base end portion connected to the main plate portion, and a fourth end that is one end connected to a third end that is the other end of the base end, and a fifth end that is the other end serving as a tip end of the insertion part. and, when a virtual line that passes through the through hole and is perpendicular to the main plate portion is defined as a first virtual line, in each of the base ends, the third end is disposed at a position furthest from the first virtual line, and in each of the tip ends, the fourth end is disposed at a position furthest from the first virtual line, each of the insertion portions has a connection portion that is a connection point between the third end of the base end and the fourth end of the tip end and is in contact with an inner circumferential surface of the rotating shaft and is fixed to the rotating shaft, and one of the insertion portions is configured to have a blade portion formed by twisting a plate-shaped member and connected to the fifth end .

The compressor according to the present disclosure comprises a rotating electric machine, a rotating shaft connected to the rotating electric machine and rotated by the power of the rotating electric machine, a compression mechanism connected to the rotating shaft and compressing a refrigerant drawn in from the outside with the power of the rotating electric machine transmitted by the rotating shaft, a compressor outer shell that houses the rotating electric machine, the rotating shaft and the compression mechanism and stores refrigeration oil therein, and an oil supply part according to the present disclosure, wherein the rotating shaft has an oil supply hole that opens at one end and supplies the refrigeration oil drawn in to the compression mechanism, each of the insertion parts of the oil supply part is inserted into the oil supply hole, the connection parts of each of the insertion parts are in contact with the inner surface of the rotating shaft, and the oil supply part is fixed to the rotating shaft.

In addition, the refrigeration cycle device according to the present disclosure includes a compressor according to the present disclosure, a radiator in which the refrigerant compressed by the compressor radiates heat, a pressure reducer that reduces the pressure of the refrigerant flowing out from the radiator, and an evaporator in which the refrigerant flowing out from the pressure reducer evaporates.

In the oil supply part according to the present disclosure, when the oil supply part is fixed to the rotating shaft, each of the insertion parts is inserted into the oil supply hole of the rotating shaft while the outer surface of each connection part of the insertion parts contacts the inner peripheral surface of the rotating shaft. Therefore, the oil supply part according to the present disclosure can reduce resistance when each of the insertion parts is inserted into the oil supply hole of the rotating shaft compared to conventional methods. Therefore, the oil supply part according to the present disclosure can be attached to the rotating shaft of a compressor more easily than conventional methods.

1 is a vertical cross-sectional view showing an overall configuration of a compressor according to a first embodiment. 1 is a diagram showing a refrigeration cycle device according to a first embodiment; 1 is a vertical cross-sectional view showing a state in which an oil supply part according to a first embodiment is attached to an end of a rotating shaft of a compressor. FIG. FIG. 2 is a vertical cross-sectional view showing the fuel supply part according to the first embodiment. FIG. 2 is a plan view showing the fuel supply part according to the first embodiment. 1 is a schematic diagram showing a state in which a fuel supply part according to a first embodiment is observed from the side; FIG. FIG. 11 is a schematic diagram showing a fuel supply part according to a comparative example as viewed from the side. FIG. 11 is a schematic diagram showing a fuel supply part according to a comparative example as viewed from the side. FIG. 11 is a vertical cross-sectional view showing a fuel supply part according to a second embodiment. FIG. 11 is a bottom view showing a fuel supply part according to a second embodiment.

Embodiment 1.
FIG. 1 is a vertical cross-sectional view showing the overall configuration of a compressor according to a first embodiment.
[Configuration of Compressor 1]
As shown in FIG. 1, the compressor 1 according to the first embodiment is a rolling piston type compressor as an example of a compressor according to the present disclosure. The compressor 1 includes a compressor housing 10, a first suction pipe 2A, a second suction pipe 2B, a suction muffler 3, a compression mechanism 20, a rotating electric machine 30, a rotating shaft 40, and a discharge pipe 4. The compressor housing 10 constitutes the housing of the compressor 1. The first suction pipe 2A and the second suction pipe 2B supply refrigerant into the compressor housing 10. The suction muffler 3 is connected to the first suction pipe 2A and the second suction pipe 2B. The compression mechanism 20 is connected to the first suction pipe 2A and the second suction pipe 2B and compresses the refrigerant. The rotating electric machine 30 includes a rotor 31 and a stator 32. The rotating shaft 40 is connected to the rotor 31 of the rotating electric machine 30 and rotates together with the rotor 31. The discharge pipe 4 discharges the refrigerant compressed in the compression mechanism 20 to the outside of the compressor shell 10 .
The configuration of the compressor 1 will be described in detail below.

(Compressor shell 10)
The compressor outer casing 10, which constitutes the outer casing of the compressor 1, houses a compression mechanism 20, a rotating electric machine 30, a rotating shaft 40, etc. The compressor outer casing 10 includes a head 11, a bottom 13, and a body 12. The head 11 constitutes the outer casing of the upper part of the compressor 1. The bottom 13 constitutes the outer casing of the lower part of the compressor 1. The body 12 constitutes the outer casing of the middle part of the compressor 1, with the head 11 attached to the upper part and the bottom 13 attached to the lower part.

The head 11 constituting the upper part of the compressor outer casing 10 is, for example, approximately bowl-shaped, as shown in Figure 1. The head 11 is connected to a discharge pipe 4 that connects the inside and outside of the compressor outer casing 10.

The body 12 constituting the middle part of the compressor outer casing 10 has, for example, a substantially cylindrical shape as shown in FIG. 1. The body 12 is connected to a first suction pipe 2A and a second suction pipe 2B for supplying refrigerant into the compressor outer casing 10. The stator 32 of the rotating electric machine 30 is attached to the inner circumferential surface of the body 12. The compression mechanism 20 is attached to the inner circumferential surface of the body 12. In the first embodiment, a rolling piston type compression mechanism is used as the compression mechanism 20. In such a case, the compression mechanism 20 is often attached to the inner circumferential surface of the body 12 below the position where the stator 32 is attached.

The bottom 13 constituting the lower part of the compressor outer casing 10 is, for example, roughly bowl-shaped, as shown in Figure 1. Refrigeration oil 6, which is a lubricating oil, is stored in the bottom 13. That is, refrigeration oil 6 is stored inside the compressor outer casing 10. This refrigeration oil 6 is then supplied to the compression mechanism 20 etc., reducing friction at the sliding parts of the compression mechanism 20 etc.

(First intake pipe 2A and second intake pipe 2B)
As described above, the first suction pipe 2A and the second suction pipe 2B are connected to the body 12 of the compressor housing 10. One end of the first suction pipe 2A is connected to a first cylinder 21A of the compression mechanism 20, which will be described later. The other end of the first suction pipe 2A is connected to the suction muffler 3. One end of the second suction pipe 2B is connected to a second cylinder 21B of the compression mechanism 20, which will be described later. The other end of the second suction pipe 2B is connected to the suction muffler 3.

(Intake muffler 3)
The suction muffler 3 functions as a muffler that reduces refrigerant noise and the like generated when the refrigerant flows into the compressor 1. The suction muffler 3 also functions as an accumulator that can store liquid refrigerant. As described above, the suction muffler 3 communicates with the first suction pipe 2A and the second suction pipe 2B.

(Compression mechanism 20)
The compression mechanism 20 is connected to the rotating shaft 40, and compresses the refrigerant sucked from the outside by the power of the rotating electric machine 30 transmitted by the rotating shaft 40. In the first embodiment, the refrigerant flowing into the suction muffler 3 is supplied to the compression mechanism 20 through the first suction pipe 2A and the second suction pipe 2B. That is, the compression mechanism 20 sucks the external refrigerant through the first suction pipe 2A and the second suction pipe 2B and compresses the refrigerant. The refrigerant compressed by the compression mechanism 20 is released into the compressor housing 10. As described above, in the first embodiment, a rolling piston type compression mechanism is adopted as the compression mechanism 20. For this reason, the compression mechanism 20 includes a cylinder that compresses the refrigerant sucked from the outside. In the first embodiment, the compression mechanism 20 includes a first cylinder 21A and a second cylinder 21B as cylinders. The first cylinder 21A is connected to the first suction pipe 2A and compresses the refrigerant supplied from the first suction pipe 2A. The second cylinder 21B is in communication with the second suction pipe 2B and compresses the refrigerant supplied from the second suction pipe 2B.

The first cylinder 21A is provided with a first piston 22A that rotates slidably within the first cylinder 21A. This first piston 22A is connected to the rotating shaft 40 so as to be able to rotate eccentrically with respect to the center of rotation of the rotating shaft 40 within the first cylinder 21A. Hereinafter, the rotational motion eccentric with respect to the center of rotation of the rotating shaft 40 is referred to as eccentric rotational motion. In addition, the second cylinder 21B is provided with a second piston 22B that rotates slidably within the second cylinder 21B. This second piston 22B is connected to the rotating shaft 40 so as to be able to rotate eccentrically within the second cylinder 21B.

In addition, the first piston 22A is connected to the rotating shaft 40 so that it can rotate in the first cylinder 21A with a phase shift of 180 degrees relative to the rotation phase when the second piston 22B rotates in the second cylinder 21B. In other words, the second piston 22B is connected to the rotating shaft 40 so that it can rotate in the second cylinder 21B with a phase shift of -180 degrees relative to the rotation phase when the first piston 22A rotates in the first cylinder 21A.

An upper bearing 24A that rotatably supports the rotating shaft 40 is provided on the upper side of the first cylinder 21A. The upper bearing 24A closes the upper opening of the first cylinder 21A. A partition plate 25 is provided on the lower side of the first cylinder 21A. The partition plate 25 closes the lower opening of the first cylinder 21A and closes the upper opening of the second cylinder 21B. In other words, the partition plate 25 separates the space formed by the first cylinder 21A and the first piston 22A from the space formed by the second cylinder 21B and the second piston 22B. On the other hand, a lower bearing 24B that rotatably supports the rotating shaft 40 is provided on the lower side of the second cylinder 21B. The lower bearing 24B closes the lower opening of the second cylinder 21B.

The upper bearing 24A is provided with a valve (not shown) that releases the refrigerant compressed by the first cylinder 21A and the first piston 22A. When this valve is opened, it is possible to connect the space formed by the first cylinder 21A and the first piston 22A to the first muffler 23A described below. The lower bearing 24B is provided with a valve (not shown) that releases the refrigerant compressed by the second cylinder 21B and the second piston 22B. When this valve is opened, it is possible to connect the space formed by the second cylinder 21B and the second piston 22B to the second muffler 23B described below.

The upper bearing 24A is provided with a first muffler 23A from which the refrigerant compressed by the first cylinder 21A and the first piston 22A is discharged. The first muffler 23A is provided with a refrigerant discharge section (not shown). As a result, the refrigerant compressed by the first cylinder 21A and the first piston 22A is discharged into the first muffler 23A and then released from the refrigerant discharge section into the inside of the compressor outer shell 10. The lower bearing 24B is provided with a second muffler 23B from which the refrigerant compressed by the second cylinder 21B and the second piston 22B is discharged. The second muffler 23B is connected to the first muffler 23A through a refrigerant flow path (not shown). As a result, the refrigerant compressed by the second cylinder 21B and the second piston 22B is discharged into the second muffler 23B and then flows into the first muffler 23A through a refrigerant flow path (not shown). The refrigerant that has flowed into the first muffler 23A is discharged into the inside of the compressor housing 10 from a refrigerant discharge portion of the first muffler 23A.

(Rotating Electric Machine 30 and Rotating Shaft 40)
The rotating electric machine 30 has a rotor 31 that transmits its own rotation to a rotating shaft 40, and a stator 32 that is configured by mounting multiple phase windings on a laminated core.

The rotating shaft 40 is connected to the rotating electric machine 30 and rotates by the power of the rotating electric machine 30. The rotating shaft 40 also transmits the power of the rotating electric machine 30 to the compression mechanism 20. In this embodiment 1, the upper end side of the rotating shaft 40 is connected to the rotor 31 of the rotating electric machine 30. As a result, the rotating shaft 40 rotates together with the rotation of the rotor 31. The rotating shaft 40 shown in FIG. 1 rotates around an axis extending in the vertical direction of the paper as the center of rotation. The lower end side of the rotating shaft 40 is connected to the compression mechanism 20. More specifically, the lower end side of the rotating shaft 40 is rotatably supported by the upper bearing 24A and the lower bearing 24B of the compression mechanism 20. The first piston 22A and the second piston 22B are connected between the part rotatably supported by the upper bearing 24A and the part rotatably supported by the lower bearing 24B so that they can rotate eccentrically. As a result, the rotating shaft 40 also rotates in conjunction with the rotation of the rotor 31, and the first piston 22A and the second piston 22B perform eccentric rotational motion. The refrigerant is compressed by the first cylinder 21A and the first piston 22A, and the refrigerant is compressed by the second cylinder 21B and the second piston 22B. In other words, the compression mechanism 20 compresses the refrigerant sucked in from the outside by the power of the rotating electric machine 30 transmitted by the rotating shaft 40.

(Discharge pipe 4)
The discharge pipe 4 is a pipe that discharges the refrigerant compressed by the compression mechanism 20 to the outside of the compressor shell 10. In other words, the discharge pipe 4 is a pipe that discharges the high-temperature and high-pressure refrigerant in the compressor shell 10 to the outside of the compressor shell 10.

(Centrifugal pump 45)
The rotating shaft 40 has an oil supply hole 42 that opens at an end 41, which is one end of the rotating shaft 40. The end 41 corresponds to a first end. In the first embodiment, the end 41 is the lower end of the rotating shaft 40. The oil supply hole 42 extends along the rotation center of the rotating shaft 40. The rotating shaft 40 also has a first oil supply port 43 and a second oil supply port 44. The first oil supply port 43 and the second oil supply port 44 serve as flow paths for supplying the refrigeration oil 6 sucked into the oil supply port 42 to the sliding part of the compression mechanism 20. One end of the first oil supply port 43 and the second oil supply port 44 communicates with the oil supply hole 42. The other end of the first oil supply port 43 and the second oil supply port 44 opens at a location on the outer circumferential surface of the rotating shaft 40 that faces the compression mechanism 20. In the first embodiment, the other end of first oil feed port 43 opens at a position facing upper bearing 24A of compression mechanism 20. Moreover, the other end of second oil feed port 44 opens at a position facing lower bearing 24B of compression mechanism 20.

The centrifugal pump 45 is provided inside the oil supply hole 42 of the rotating shaft 40. The centrifugal pump 45 is formed by twisting a plate-shaped member. The centrifugal pump 45 is a fluid machine that sucks up the refrigeration oil 6 as a lubricant stored in the bottom 13 of the compressor outer casing 10 by the centrifugal force generated by the rotational motion of the rotating shaft 40. The refrigeration oil 6 sucked up to the oil supply hole 42 by the centrifugal pump 45 is supplied to the sliding part of the compression mechanism 20. Specifically, a part of the refrigeration oil 6 sucked up to the oil supply hole 42 is supplied to the sliding part between the upper bearing 24A of the compression mechanism 20 and the rotating shaft 40 through the first oil supply port 43. In addition, a part of the refrigeration oil 6 sucked up to the oil supply hole 42 is supplied to the sliding part between the lower bearing 24B of the compression mechanism 20 and the rotating shaft 40 through the second oil supply port 44. As the refrigeration oil 6, for example, mineral oil-based, alkylbenzene-based, polyalkylene glycol-based, polyvinyl ether-based, polyol ester-based lubricating oil, or the like is used.

[Operation of Rotating Electric Machine 30]
A current is supplied from a power source (not shown) to the windings provided on the laminated core of the stator 32, forming a rotating magnetic field in the stator 32. This causes the rotating magnetic field of the stator 32 to act on the permanent magnets provided in the rotor 31, causing the rotor 31 to rotate. The rotation of the rotor 31 is transmitted to the first piston 22A and the second piston 22B via the rotating shaft 40, causing the first piston 22A and the second piston 22B to perform eccentric rotational motion.

[Refrigerant flow]
The eccentric rotation of the first piston 22A and the second piston 22B draws the refrigerant into the compressor 1. Specifically, the eccentric rotation of the first piston 22A and the second piston 22B causes the low-pressure refrigerant outside the compressor 1 to flow into the suction muffler 3. Then, of the low-pressure refrigerant that has flowed into the suction muffler 3, the low-pressure gaseous refrigerant flows into the compression mechanism 20 of the compressor 1 through the first suction pipe 2A and the second suction pipe 2B. A part of the gaseous refrigerant that has flowed into the compression mechanism 20 is compressed by the first cylinder 21A and the first piston 22A to become a high-temperature, high-pressure gaseous refrigerant. This high-temperature, high-pressure gaseous refrigerant flows into the first muffler 23A through the valve of the upper bearing 24A. The high-temperature, high-pressure gaseous refrigerant that has flowed into the first muffler 23A is discharged into the space inside the compressor shell 10 from a refrigerant discharge portion (not shown) provided in the first muffler 23A. The high-temperature, high-pressure gaseous refrigerant discharged into the space within the compressor shell 10 moves to the upper part of the space within the compressor shell 10 through gaps between the rotating electric machine 30 and other components, and is discharged from the discharge pipe 4.

The remainder of the gaseous refrigerant that has flowed into the compression mechanism 20 is compressed by the second cylinder 21B and the second piston 22B to become a high-temperature, high-pressure gaseous refrigerant. This high-temperature, high-pressure gaseous refrigerant flows into the second muffler 23B through the valve of the lower bearing 24B. The high-temperature, high-pressure gaseous refrigerant that has flowed into the second muffler 23B is sent from the second muffler 23B through a refrigerant flow path (not shown) to the first muffler 23A. The high-temperature, high-pressure gaseous refrigerant sent into the first muffler 23A is then discharged into the space within the compressor outer shell 10 from a refrigerant discharge section (not shown) provided in the first muffler 23A. The high-temperature, high-pressure gaseous refrigerant discharged into the space within the compressor outer shell 10 moves to the upper part of the space within the compressor outer shell 10 through gaps such as the rotating electric machine 30, and is discharged from the discharge piping 4.

In addition, the refrigeration oil 6 stored in the bottom 13 inside the compressor outer casing 10 is sucked up from the lower end of the oil supply hole 42 by the centrifugal pump 45 that rotates together with the rotating shaft 40. The refrigeration oil 6 sucked up from the lower end of the oil supply hole 42 flows as lubricating oil between the upper bearing 24A and the rotating shaft 40 from the first oil supply port 43. In addition, the refrigeration oil 6 flows from the second oil supply port 44 between the lower bearing 24B and the rotating shaft 40. By the refrigeration oil 6 flowing between these, the rotating shaft 40 can smoothly transmit the rotational driving force to the first piston 22A and the second piston 22B.

In addition, a portion of the refrigeration oil 6 that flows from the first oil supply port 43 between the upper bearing 24A and the rotating shaft 40 flows between the upper bearing 24A and the upper surface of the first piston 22A. In addition, a portion of the refrigeration oil 6 that flows from the second oil supply port 44 between the lower bearing 24B and the rotating shaft 40 flows between the lower bearing 24B and the lower surface of the second piston 22B. The refrigeration oil 6 is used to smoothly rotate the first piston 22A and the second piston 22B, but a portion of the refrigeration oil 6 is compressed together with the low-pressure gaseous refrigerant and is discharged in a state contained in the high-temperature, high-pressure gaseous refrigerant.

[Configuration and operation of the refrigeration cycle device 200]
FIG. 2 is a diagram showing the refrigeration cycle device according to the first embodiment.
The refrigeration cycle device 200 includes a compressor 1 according to the first embodiment, a radiator in which the refrigerant compressed by the compressor 1 dissipates heat, a pressure reducer 203 such as an electric expansion valve that reduces the pressure of the refrigerant flowing out from the radiator, and an evaporator in which the refrigerant flowing out from the pressure reducer 203 evaporates.

The refrigeration cycle device 200 is used for various purposes such as a hot water supply device and a refrigeration device. FIG. 2 shows an example in which the refrigeration cycle device 200 is used as an air conditioning device. For this reason, the refrigeration cycle device 200 shown in FIG. 2 is provided with an indoor heat exchanger 204 that functions as a radiator during heating operation, and an outdoor heat exchanger 202 that functions as an evaporator during heating operation. The refrigeration cycle device 200 shown in FIG. 2 is also capable of cooling operation. For this reason, the refrigeration cycle device 200 is provided with a four-way switching valve 201. The four-way switching valve 201 switches the heat exchanger connected to the discharge pipe 4, which is the discharge port of the refrigerant of the compressor 1, and switches the heat exchanger connected to the suction muffler 3, which is the suction port of the refrigerant of the compressor 1. During cooling operation, the indoor heat exchanger 204 functions as an evaporator, and the outdoor heat exchanger 202 functions as a radiator.

When the refrigeration cycle apparatus 200 is used as an air-conditioning apparatus, for example, the indoor heat exchanger 204 is mounted in an indoor apparatus. Also, for example, the four-way switching valve 201, the outdoor heat exchanger 202, and the pressure reducer 203 are mounted in an outdoor apparatus. Also, for example, the refrigeration cycle apparatus 200 uses R407C refrigerant, R410A refrigerant, R32 refrigerant, or the like.
The operation of the refrigeration cycle apparatus 200 during heating operation and cooling operation will be described below.

When the refrigeration cycle device 200 performs heating operation, the four-way switching valve 201 switches to the flow path shown by the solid line in FIG. 2. As a result, the discharge pipe 4 of the compressor 1 is connected to the indoor heat exchanger 204, and the suction muffler 3 of the compressor 1 is connected to the outdoor heat exchanger 202. That is, the indoor heat exchanger 204 functions as a radiator, and the outdoor heat exchanger 202 functions as an evaporator. In this state, when the high-temperature, high-pressure gaseous refrigerant compressed by the compressor 1 is discharged from the compressor 1, this high-temperature, high-pressure gaseous refrigerant flows into the indoor heat exchanger 204. The high-temperature, high-pressure gaseous refrigerant that flows into the indoor heat exchanger 204 condenses while releasing heat to the indoor air, and flows out of the indoor heat exchanger 204 as a high-pressure liquid refrigerant. At this time, the air in the room is warmed. Note that, depending on the type of refrigerant, such as carbon dioxide refrigerant, there are refrigerants that do not condense when releasing heat. When a refrigerant that condenses when radiating heat is used, the radiator may be called a condenser.

The high-pressure liquid refrigerant flowing out from the indoor heat exchanger 204 flows into the pressure reducer 203. The high-pressure liquid refrigerant flowing into the pressure reducer 203 is depressurized by the pressure reducer 203 to become a low-temperature, low-pressure two-phase gas-liquid refrigerant, which flows out from the pressure reducer 203. The low-temperature, low-pressure two-phase gas-liquid refrigerant flowing out from the pressure reducer 203 flows into the outdoor heat exchanger 202. The low-temperature, low-pressure two-phase gas-liquid refrigerant flowing into the outdoor heat exchanger 202 absorbs heat from the outdoor air, evaporates, and flows out from the outdoor heat exchanger 202 as a low-pressure gaseous refrigerant or a two-phase gas-liquid refrigerant. The low-pressure gaseous refrigerant or two-phase gas-liquid refrigerant flowing out from the outdoor heat exchanger 202 is sucked into the suction muffler 3 of the compressor 1. Then, the low-pressure gaseous refrigerant among the refrigerant sucked into the suction muffler 3 of the compressor 1 is compressed by the compression mechanism 20 of the compressor 1 to become a high-temperature, high-pressure gaseous refrigerant. This high-temperature, high-pressure gaseous refrigerant is discharged again from the compressor 1. That is, when the refrigeration cycle apparatus 200 performs a heating operation, the refrigerant circulates as shown by the solid arrows in FIG. 2.

When the refrigeration cycle device 200 performs cooling operation, the four-way switching valve 201 switches to the flow path shown by the dashed line in FIG. 2. As a result, the discharge pipe 4 of the compressor 1 is connected to the outdoor heat exchanger 202, and the suction muffler 3 of the compressor 1 is connected to the indoor heat exchanger 204. That is, the outdoor heat exchanger 202 functions as a radiator, and the indoor heat exchanger 204 functions as an evaporator. In this state, when the high-temperature, high-pressure gaseous refrigerant compressed by the compressor 1 is discharged from the compressor 1, this high-temperature, high-pressure gaseous refrigerant flows into the outdoor heat exchanger 202. The high-temperature, high-pressure gaseous refrigerant that flows into the outdoor heat exchanger 202 condenses while releasing heat to the outdoor air, and flows out of the outdoor heat exchanger 202 as a high-pressure liquid refrigerant.

The high-pressure liquid refrigerant flowing out of the outdoor heat exchanger 202 flows into the pressure reducer 203. The high-pressure liquid refrigerant that flows into the pressure reducer 203 is depressurized by the pressure reducer 203 to become a low-temperature, low-pressure two-phase gas-liquid refrigerant, which flows out of the pressure reducer 203. The low-temperature, low-pressure two-phase gas-liquid refrigerant that flows out of the pressure reducer 203 flows into the indoor heat exchanger 204. The low-temperature, low-pressure two-phase gas-liquid refrigerant that flows into the indoor heat exchanger 204 absorbs heat from the indoor air and evaporates, and flows out of the indoor heat exchanger 204 as a low-pressure gaseous refrigerant or a two-phase gas-liquid refrigerant. At this time, the air in the room is cooled. The low-pressure gaseous refrigerant or two-phase gas-liquid refrigerant that flows out of the indoor heat exchanger 204 is sucked into the suction muffler 3 of the compressor 1. Then, the low-pressure gaseous refrigerant among the refrigerant sucked into the suction muffler 3 of the compressor 1 is compressed by the compression mechanism 20 of the compressor 1 to become a high-temperature, high-pressure gaseous refrigerant. This high-temperature, high-pressure gaseous refrigerant is discharged again from the compressor 1. That is, when the refrigeration cycle device 200 performs cooling operation, the refrigerant circulates as shown by the dashed arrows in FIG. 2.

(Oil supply part 100)
In the compressor 1 according to the first embodiment, in order to improve the supply capacity of the refrigeration oil 6 to the sliding parts of the compression mechanism 20 when the rotating shaft 40 is in the low rotation range, an oil supply part 100 is attached to the end part 41 of the rotating shaft 40. Details of the oil supply part 100 according to the first embodiment will be described below.

Fig. 3 is a vertical cross-sectional view showing a state in which the lubrication component according to the first embodiment is attached to an end of a rotating shaft of a compressor. Fig. 4 is a vertical cross-sectional view showing the lubrication component according to the first embodiment. Fig. 5 is a plan view showing the lubrication component according to the first embodiment.
The lubrication part 100 is formed, for example, from a metal plate-shaped member. In the present embodiment 1, the lubrication part 100 is formed using a plate-shaped member of GB-65Mn, which is a spring steel material. The material of the lubrication part 100 is not particularly limited, and the lubrication part 100 may be formed using a metal plate-shaped member such as SPCC, SUS304, or S50C.

3 to 5, the oil supply part 100 includes a main plate 110 and a plurality of insertion parts 120. The main plate 110 has, for example, a flat plate shape. A through hole 111 is formed in the main plate, for example, at a substantially central position. Each of the insertion parts 120 protrudes from a position closer to the outer periphery 112 of the main plate 110 than the through hole 111 in the main plate 110. Each of the insertion parts 120 is inserted into the oil supply hole 42 of the rotating shaft 40. In detail, the plurality of insertion parts 120 are inserted into the oil supply hole 42 of the rotating shaft 40, and the outer surfaces of the plurality of insertion parts 120 come into contact with the inner periphery 46 of the rotating shaft 40, whereby the oil supply part 100 is fixed to the end 41 of the rotating shaft 40.

In the oil supply part 100 configured in this manner, a through hole 111 is formed on the inner periphery of the multiple insertion parts 120 inserted into the oil supply hole 42. Therefore, the diameter of the through hole 111 is smaller than the diameter of the oil supply hole 42 of the rotating shaft 40. In this manner, by configuring the refrigeration oil 6 to be sucked into the oil supply hole 42 of the rotating shaft 40 from the through hole 111, which is smaller in diameter than the oil supply hole 42 of the rotating shaft 40, the supply capacity of the refrigeration oil 6 to the sliding parts of the compression mechanism 20 can be improved when the rotating shaft 40 is in the low rotation range. In other words, the reliability of the compressor 1 can be ensured when the rotating shaft 40 is in the low rotation range.

Here, conventionally, there exists an oil supply part having a main plate portion configured similarly to the main plate portion 110 of the oil supply part 100 according to the first embodiment. This conventional oil supply part has a problem in that it is difficult to attach to the rotating shaft of the compressor. Therefore, in the oil supply part 100 according to the first embodiment, each of the insertion portions 120 is configured as follows.

Specifically, each of the insertion parts 120 has a base end 121 and a tip end 125. One end of the base end 121, end 122, is connected to the main plate part 110. This end 122 is an end corresponding to the second end. One end of the tip part 125, end 126, is connected to end 123, which is the other end of the base end 121. In addition, end 127, which is the other end of the tip part 125, is the tip of the insertion part 120. Note that end 123 corresponds to the third end, end 126 corresponds to the fourth end, and end 127 corresponds to the fifth end. Hereinafter, the connection point between end 123 of the base end 121 and end 126 of the tip part 125 is referred to as connection part 130.

Each of the insertion parts 120 configured in this manner has the following posture. In describing each posture of the insertion part 120, a virtual line passing through the through hole 111 of the main plate part 110 and perpendicular to the main plate part 110 is defined as a first virtual line L1. This first virtual line L1 is a virtual line that is approximately parallel to the center of rotation of the rotating shaft 40 when the oil supply part 100 is attached to the end part 41 of the rotating shaft 40. In other words, this first virtual line L1 is a virtual line that is approximately parallel to the direction in which the oil supply hole 42 extends when the oil supply part 100 is attached to the end part 41 of the rotating shaft 40. When the first virtual line L1 is defined in this manner, in each of the base ends 121, the end part 123 is disposed at a position farthest from the first virtual line L1. In addition, in each of the tip ends 125, the end part 126 is disposed at a position farthest from the first virtual line L1. That is, in each of the insertion sections 120, the connection section 130 is disposed at a position farthest from the first virtual straight line L1.

In the lubrication part 100 in which each of the insertion parts 120 is in the above-mentioned position, the connection parts 130 and the ends 127 may be arranged as follows according to the diameter of the lubrication hole 42 of the rotating shaft 40 to which the lubrication part 100 is attached. This makes it easier to attach the lubrication part 100 to the rotating shaft 40 than in the past.

In detail, a virtual circle tangent to the outer surface of each connecting portion 130 of the insertion portion 120 is defined as a first virtual circle C1. The diameter of this first virtual circle C1 is defined as a first diameter D1. A virtual circle tangent to the outer surface of the end portion 127 of each tip portion 125 of the insertion portion 120 is defined as a second virtual circle C2. The diameter of this second virtual circle C2 is defined as a second diameter D2. The diameter of the oil supply hole 42 formed in the rotating shaft 40 is defined as a third diameter D3. When defined in this way, it is sufficient that the first diameter D1 is larger than the third diameter D3, and the second diameter D2 is smaller than the third diameter D3.

Below, we will explain why the oil supply part 100 of this embodiment 1 can be attached to the rotating shaft 40 easier than in the past, based on a schematic diagram of the oil supply part 100 of this embodiment 1 and a schematic diagram of an oil supply part of a comparative example.

Figure 6 is a schematic diagram showing the state of the fuel supply part according to the first embodiment as observed from the side. Figures 7 and 8 are schematic diagrams showing the state of the fuel supply part according to the comparative example as observed from the side. Note that Figures 6 to 8 illustrate a pair of opposing insertion portions.

6, in each of the insertion parts 120 of the fuel supply part 100 according to the present embodiment 1, as described above, in each of the base ends 121, the end 123 is disposed at a position farthest from the first virtual straight line L1. In addition, in each of the tip ends 125, the end 126 is disposed at a position farthest from the first virtual straight line L1.

In each of the insertion portions 320 of the fuel supply part 300 according to the comparative example shown in Figure 7, the base end 321 has the same distance from the first imaginary line L1 over the entire area. The tip end 325 also has the same distance from the first imaginary line L1 over the entire area. That is, in the fuel supply part 300 according to the comparative example shown in Figure 7, the insertion portions 320 extend parallel to the first imaginary line L1 from the main plate portion 310. Also, each of the insertion portions 320 is parallel. The engagement claw of the fuel supply part described in Japanese Utility Model Publication No. 63-154787, which is listed as a document disclosing prior art, has the same shape as the insertion portion 320 shown in Figure 7.

In each of the insertion portions 420 of the fuel supply part 400 according to the comparative example shown in Figure 8, the base end 421 has the same distance from the first imaginary line L1 over the entire area. Furthermore, the distance of the tip end 425 from the first imaginary line L1 decreases from the base end 421 side toward the tip end. That is, in the fuel supply part 400 according to the comparative example shown in Figure 8, the base end 421 of the insertion portion 420 extends from the main plate portion 410 in parallel to the first imaginary line L1. Furthermore, each of the base ends 421 of the insertion portion 420 is parallel to each other.

When attaching a lubrication part to a rotating shaft, first, each of the insertion parts of the lubrication part is inserted into the lubrication hole of the rotating shaft so that the outer surface of each insertion part is in contact with the inner surface of the rotating shaft. Then, each insertion part is inserted into the lubrication hole until the lubrication part is in the specified attachment position. Each insertion part whose outer surface is in contact with the inner surface of the rotating shaft is pressed by the inner surface of the rotating shaft and deformed. As a result, a spring force is generated in each insertion part whose outer surface is in contact with the inner surface of the rotating shaft. The spring force of the insertion part is the reaction force generated in the insertion part when the deformed insertion part tries to return to its original shape. The spring force of each insertion part inserted into the lubrication hole of the rotating shaft fixes the lubrication part to the rotating shaft. In this way, the lubrication part is attached to the rotating shaft.

Here, in the lubrication part 300 according to the comparative example shown in FIG. 7, each of the insertion parts 320 extends parallel to the first virtual straight line L1. Therefore, when the lubrication part 300 according to the comparative example shown in FIG. 7 is fixed to the rotating shaft 40 as described above, the diameter of the virtual circle tangent to the outer surface of each of the tip ends of the insertion parts 320 needs to be larger than the third diameter D3, which is the diameter of the lubrication hole 42. Therefore, in the lubrication part 300 according to the comparative example shown in FIG. 7, it is difficult to insert each tip end of the insertion part 320 into the lubrication hole 42. Also, in the lubrication part 300 according to the comparative example shown in FIG. 7, each of the insertion parts 320 is inserted into the lubrication hole 42 while most of the outer surface of each of the insertion parts 320 is in contact with the inner surface 46 of the rotating shaft 40 until the lubrication part 300 reaches the specified mounting position. Therefore, in the lubrication part 300 according to the comparative example shown in FIG. 7, the resistance when inserting each of the insertion parts 320 into the lubrication hole 42 becomes large. Therefore, it is difficult to attach the lubrication part 300 according to the comparative example shown in FIG.

In the lubrication part 400 according to the comparative example shown in FIG. 8, the distance from the first virtual straight line L1 of each of the tip portions 425 decreases from the base end portion 421 side toward the tip portion. Therefore, in the lubrication part 400 according to the comparative example shown in FIG. 8, the diameter of the virtual circle tangent to the outer surface of each tip portion 425 may be smaller than the third diameter D3, which is the diameter of the lubrication hole 42. Even if each tip portion of the tip portion 425 is positioned in such a position, when the insertion portion 420 is inserted into the lubrication hole 42, each outer surface of the base end portion 421 can contact the inner peripheral surface 46 of the rotating shaft 40. Therefore, the lubrication part 400 according to the comparative example shown in FIG. 8 makes it easier to insert each tip portion of the insertion portion 420 into the lubrication hole 42, compared to the lubrication part 300 according to the comparative example shown in FIG. 7.

However, in the lubrication part 400 according to the comparative example shown in FIG. 8, each of the base ends 421 of the insertion parts 420 extends parallel to the first virtual straight line L1. Therefore, in the lubrication part 400 according to the comparative example shown in FIG. 8, each of the insertion parts 420 is inserted into the lubrication hole 42 while most of the outer surface of each of the base ends 421 is in contact with the inner surface 46 of the rotating shaft 40 until the lubrication part 400 reaches the specified mounting position. Therefore, the lubrication part 400 according to the comparative example shown in FIG. 8 has a large resistance when inserting each of the insertion parts 420 into the lubrication hole 42. Therefore, the lubrication part 400 according to the comparative example shown in FIG. 8 is also difficult to attach to the rotating shaft 40, like the lubrication part 300 according to the comparative example shown in FIG. 7.

On the other hand, in the lubrication part 100 according to the first embodiment, as described above, the second diameter D2 of the second virtual circle C2 tangent to the outer surface of each of the ends 127 at the tip of the insertion part 120 can be made smaller than the third diameter D3, which is the diameter of the lubrication hole 42. Therefore, the lubrication part 100 according to the first embodiment makes it easy to insert each of the ends 127 at the tip of the insertion part 120 into the lubrication hole 42. At this time, in the lubrication part 100 according to the first embodiment, as described above, the first diameter D1 of the first virtual circle C1 tangent to the outer surface of each of the connection parts 130 of the insertion part 120 can be made larger than the third diameter D3, which is the diameter of the lubrication hole 42. Therefore, even if the second diameter D2 is made smaller than the third diameter D3, it is possible to attach the lubrication part 100 according to the first embodiment to the rotating shaft 40.

In addition, in the lubrication part 100 according to the first embodiment, each of the insertion parts 120 is inserted into the lubrication hole 42 while only the outer surface of each of the connection parts 130 of the insertion parts 120 contacts the inner surface 46 of the rotating shaft 40 until the lubrication part 100 reaches the specified mounting position. That is, each of the connection parts 130 of the insertion parts 120 contacts the inner surface 46 of the rotating shaft 40 and is fixed to the rotating shaft 40. For this reason, the lubrication part 100 according to the first embodiment can reduce the resistance when each of the insertion parts 120 is inserted into the lubrication hole 42. Therefore, the lubrication part 100 according to the first embodiment can be attached to the rotating shaft 40 more easily than before.

In this embodiment 1, as shown in FIG. 4, the base end 121 and the tip end 125 are formed with inclined surfaces to configure each of the insertion parts 120 into the above-mentioned shape. In detail, each of the base ends 121 is connected to the end 126 of the tip end 125 and has a first inclined surface portion 124 that approaches the first virtual straight line L1 from the end 123 to the end 122. Also, each of the tip ends 125 is connected to the end 123 of the base end 121 and has a second inclined surface portion 128 that approaches the first virtual straight line L1 from the end 126 to the end 127. Also, the entire base end 121 may be the first inclined surface portion 124, or a part of the base end 121 may be the first inclined surface portion 124. Also, the entire tip end 125 may be the second inclined surface portion 128, or a part of the tip end 125 may be the second inclined surface portion 128. By configuring the insertion portion 120 in this manner using the first inclined surface portion 124 and the second inclined surface portion 128, the formation of the insertion portion 120 becomes simple, and the manufacture of the fuel supply part 100 becomes easy.

In addition, when the insertion part 120 is configured using the first inclined surface portion 124 and the second inclined surface portion 128, it is preferable that the angles of the first inclined surface portion 124 and the second inclined surface portion 128 are set as follows. Below, the suitable angles of the first inclined surface portion 124 and the second inclined surface portion 128 are explained using the schematic diagram of the oil supply part 100 shown in Figure 6.

6, the virtual line that is tangent to the outer surface of the connection portion 130 and parallel to the first virtual line L1 is defined as the second virtual line L2. When defined in this way, it is preferable that the angle β between the second virtual line L2 and the second inclined surface portion 128 of the tip portion 125 is larger than the angle α between the second virtual line L2 and the first inclined surface portion 124 of the base end portion 121. This is because the first inclined surface portion 124 only needs to be at an angle such that the base end portion 121 does not contact the inner surface 46 of the rotating shaft 40 when the insertion portion 120 is inserted into the oil supply hole 42 of the rotating shaft 40. On the other hand, it is preferable that the end portion 127, which is the tip of the tip portion 125, is positioned at a position where the second diameter D2 is as small as possible so that it is easy to insert it into the oil supply hole 42 of the rotating shaft 40. Therefore, it is preferable that the angle β between the second imaginary straight line L2 and the second inclined surface portion 128 of the tip end portion 125 is larger than the angle α between the second imaginary straight line L2 and the first inclined surface portion 124 of the base end portion 121.

As shown in Figs. 3 to 6, the oil supply part 100 is preferably provided with at least one contact part 140 that is provided on the outer periphery 112 of the main plate part 110 and contacts the end part 41 of the rotating shaft 40. In the present embodiment 1, the contact parts 140 are provided between the insertion parts 120, and a total of four contact parts 140 are provided. When each of the insertion parts 120 is inserted into the oil supply hole 42 of the rotating shaft 40, the oil supply part 100 stops at the position where the contact part 140 contacts the end part 41 of the rotating shaft 40. Therefore, by providing the contact part 140 to the oil supply part 100, it is easy to position the oil supply part 100 when attaching it to the rotating shaft 40. In addition, by providing the contact part 140 to the oil supply part 100, it is also possible to prevent the oil supply part 100 from entering the inside of the oil supply hole 42 while the compressor 1 is in operation. Therefore, by providing the oil supply part 100 with the contact portion 140, the reliability of the compressor 1 is improved.

The number of the insertion parts 120 provided in the refueling part 100 is not particularly limited as long as it is multiple. That is, the number of the insertion parts 120 provided in the refueling part 100 may be two or more. However, the number of the insertion parts 120 is preferably four. In addition, it is preferable that two of the four insertion parts 120 are arranged opposite each other, and the remaining two insertion parts 120 are arranged opposite each other. In detail, the refueling part 100 is fixed to the rotating shaft 40 by the spring force of the insertion parts 120. Therefore, the fewer the number of the insertion parts 120, the more rigidity of the insertion parts 120 needs to be increased, and the greater the force required to deform the insertion parts 120. In other words, the greater the force required to insert the insertion parts 120 into the refueling hole 42. On the other hand, if the number of the insertion parts 120 is too large, the spring force of each insertion part 120 becomes weak, and the stability of the refueling part 100 when fixed to the rotating shaft 40 decreases. Furthermore, in order to stably fix the oil supply part 100 to the rotating shaft 40, it is preferable that the spring force of the insertion parts 120 acts axially symmetrically on the inner peripheral surface 46 of the rotating shaft 40 with the extension direction of the oil supply hole 42 as the reference axis. That is, it is preferable that two insertion parts 120 are arranged opposite each other. For this reason, it is preferable that the number of insertion parts 120 provided in the oil supply part 100 is four. It is also preferable that two of the four insertion parts 120 are arranged opposite each other, and the remaining two insertion parts 120 are arranged opposite each other.

As described above, the oil supply part 100 according to the first embodiment is provided in a compressor 1 having an oil supply hole 42 opening at an end 41 and a rotating shaft 40 that supplies the refrigeration oil 6 sucked into the oil supply hole 42 to the compression mechanism 20. The oil supply part 100 has a main plate portion 110 and a plurality of insertion portions 120. A through hole 111 is formed in the main plate portion 110. Each of the insertion portions 120 protrudes from a position on the outer periphery 112 side of the main plate portion 110 relative to the through hole 111 in the main plate portion 110, and is inserted into the oil supply hole 42. Each of the insertion portions 120 has a base end portion 121 and a tip portion 125. The base end portion 121 has an end portion 122 connected to the main plate portion 110. The tip portion 125 is a portion in which the end portion 126 is connected to the end portion 123 of the base portion 121, and the end portion 127 is the tip of the insertion portion 120. If a virtual line passing through the through hole 111 and perpendicular to the main plate portion 110 is defined as a first virtual line L1, in each of the base portions 121, the end portion 123 is disposed at a position farthest from the first virtual line L1. In addition, in each of the tip portions 125, the end portion 126 is disposed at a position farthest from the first virtual line L1. In each of the insertion portions 120 of the fuel supply part 100, the connection portion 130, which is the connection portion between the end portion 123 of the base portion 121 and the end portion 126 of the tip portion 125, contacts the inner circumferential surface 46 of the rotating shaft 40, and is fixed to the rotating shaft 40.

As described above, the oil supply part 100 configured in this manner makes it easier to insert each of the ends 127, which are the tips of the insertion parts 120, into the oil supply hole 42. Furthermore, as described above, the oil supply part 100 configured in this manner can reduce the resistance when inserting each of the insertion parts 120 into the oil supply hole 42. Therefore, the oil supply part 100 configured in this manner can be attached to the rotating shaft 40 more easily than before.

Embodiment 2.
By configuring the oil supply component 100 as follows, it is possible to reduce the number of components of the compressor 1 and the number of assembly steps for the compressor 1, as compared to the first embodiment. In the second embodiment, items that are not specifically described are the same as those in the first embodiment, and the same functions and configurations as those in the first embodiment are described using the same reference numerals.

Fig. 9 is a vertical cross-sectional view showing the lubrication part according to the second embodiment, and Fig. 10 is a bottom view showing the lubrication part according to the second embodiment.
In the fuel supply part 100 according to the second embodiment, one of the insertion parts 120 is provided with a blade part 145 formed by twisting a plate-shaped member and connected to an end part 127 of the tip part 125 .

9 and 10 indicates the position that will be the center of the oil supply hole 42 when the oil supply part 100 is attached to the rotating shaft 40. The shape of the blade portion 145, which is a plate-shaped member, is observed from the end portion on the end 127 side of the insertion part 120 to the end portion on the opposite side of the end portion. In this case, the blade portion 145 extends from one end portion 127 of the insertion part 120 toward the third virtual straight line L3. It also bends at the position of the third virtual straight line L3, and then extends along the third virtual straight line L3. The blade portion 145, which is a plate-shaped member, is twisted at the portion extending along the third virtual straight line L3. When the oil supply part 100 is attached to the rotating shaft 40, the twisted portion of the blade portion 145 is disposed inside the oil supply hole 42 and functions as a centrifugal pump.

That is, the oil supply part 100 according to the second embodiment is configured to have a centrifugal pump integrally formed therewith. Therefore, in a compressor 1 in which the oil supply part 100 according to the second embodiment is provided, the centrifugal pump 45 shown in the first embodiment is not necessary. Therefore, by adopting the oil supply part 100 according to the second embodiment, the number of parts of the compressor 1 can be reduced. In addition, by attaching the oil supply part 100 according to the second embodiment to the rotating shaft 40, the centrifugal pump is also attached to the rotating shaft 40 at the same time. Therefore, by adopting the oil supply part 100 according to the second embodiment, the assembly man-hours of the compressor 1 can also be reduced.

1 Compressor, 2A First intake pipe, 2B Second intake pipe, 3 Intake muffler, 4 Discharge pipe, 6 Refrigeration oil, 10 Compressor shell, 11 Head, 12 Body, 13 Bottom, 20 Compression mechanism, 21A First cylinder, 21B Second cylinder, 22A First piston, 22B Second piston, 23A First muffler, 23B Second muffler, 24A Upper bearing, 24B Lower bearing, 25 Partition plate, 30 Rotating electric machine, 31 Rotor, 32 Stator, 40 Rotating shaft, 41 End, 42 Oil supply hole, 43 First oil supply port, 44 Second oil supply port, 45 Centrifugal pump, 46 Inner surface, 100 Oil supply part, 110 Main plate, 111 Through hole, 112 Outer periphery, 120 Insertion portion, 121 base end portion, 122 end portion, 123 end portion, 124 first inclined surface portion, 125 tip portion, 126 end portion, 127 end portion, 128 second inclined surface portion, 130 connection portion, 140 contact portion, 145 blade portion, 200 refrigeration cycle device, 201 four-way switching valve, 202 outdoor heat exchanger, 203 pressure reducer, 204 indoor heat exchanger, 300 oil supply part (comparative example), 310 main plate portion (comparative example), 320 insertion portion (comparative example), 321 base end portion (comparative example), 325 tip portion (comparative example), 400 oil supply part (comparative example), 410 main plate portion (comparative example), 420 insertion portion (comparative example), 421 base end portion (comparative example), 425 tip portion (comparative example), C1 first imaginary circle, C2 second imaginary circle, D1 first diameter, D2 Second diameter, D3 third diameter, L1 first virtual line, L2 second virtual line, L3 third virtual line.

Claims (7)

An oil supply part provided in a compressor having a rotating shaft, the rotating shaft having an oil supply hole that opens into a first end portion, the oil supply part supplying refrigeration oil sucked into the oil supply hole to a compression mechanism,
A main plate portion having a through hole formed therein;
a plurality of insertion portions protruding from positions on the outer periphery side of the main plate portion relative to the through holes and inserted into the oil supply hole;
Equipped with
Each of the insertion portions is
A base end portion, the second end portion being one end portion of the base end portion connected to the main plate portion;
a fourth end portion which is one end portion of the base end portion is connected to a third end portion which is the other end portion of the base end portion, and a fifth end portion which is the other end portion of the base end portion is a tip portion which becomes a tip of the insertion portion;
Equipped with
When a virtual line passing through the through hole and perpendicular to the main plate portion is defined as a first virtual line,
In each of the base ends, the third end is disposed at a position farthest from the first imaginary line,
In each of the tip portions, the fourth end is disposed at a position farthest from the first imaginary line,
Each of the insertion sections has a connection portion, which is a connection point between the third end of the base end and the fourth end of the tip end, contacting an inner circumferential surface of the rotating shaft and fixed to the rotating shaft ,
A fuel supply component in which one of the insertion portions is formed by twisting a plate-shaped member and has a wing portion connected to the fifth end portion . a virtual circle tangent to an outer surface of each of the connection portions of the insertion portions is defined as a first virtual circle;
The diameter of the first virtual circle is defined as a first diameter,
a virtual circle tangent to an outer surface of the fifth end of each of the tip portions of the insertion portions is defined as a second virtual circle;
The diameter of the second virtual circle is defined as a second diameter,
When the diameter of the oil supply hole formed in the rotating shaft is defined as a third diameter,
the first diameter is greater than the third diameter;
The lubrication component of claim 1 , wherein the second diameter is smaller than the third diameter. The fuel supply component according to claim 1 or 2, further comprising a contact portion provided on the outer periphery of the main plate portion and adapted to come into contact with the first end of the rotating shaft. Each of the base ends is connected to the fourth end of the tip end and includes a first inclined surface portion that approaches the first virtual straight line from the third end toward the second end,
Each of the tip portions includes a second inclined surface portion that is connected to the third end portion of the base portion and approaches the first virtual straight line from the fourth end portion toward the fifth end portion,
When a virtual line that is in contact with the outer surface of the connection portion and is parallel to the first virtual line is defined as a second virtual line,
The fuel supply component according to any one of claims 1 to 3, wherein an angle between the second virtual straight line and the second inclined surface portion is greater than an angle between the second virtual straight line and the first inclined surface portion. The insertion portion includes four of the insertion portions,
The two insertion portions are disposed opposite each other,
The fuel supply component according to any one of claims 1 to 4, wherein the remaining two insertion portions are arranged opposite each other. A rotating electric machine;
a rotating shaft connected to the rotating electric machine and rotated by the power of the rotating electric machine;
a compression mechanism connected to the rotary shaft and configured to compress a refrigerant drawn in from the outside by using the power of the rotary electric machine transmitted by the rotary shaft;
a compressor shell that houses the rotating electric machine, the rotating shaft, and the compression mechanism and stores refrigeration oil therein;
The oil supply part according to any one of claims 1 to 5 ,
Equipped with
The rotating shaft has an oil supply hole that opens at one end and supplies the refrigeration oil sucked therein to the compression mechanism,
a compressor in which each of the insertion portions of the oil supply parts is inserted into the oil supply hole, each of the connection portions of the insertion portions contacts an inner circumferential surface of the rotating shaft, and the oil supply parts are fixed to the rotating shaft. A compressor according to claim 6 ;
a radiator through which the refrigerant compressed by the compressor radiates heat;
a pressure reducer that reduces the pressure of the refrigerant flowing out from the radiator;
an evaporator in which the refrigerant flowing out from the pressure reducer evaporates;
A refrigeration cycle device comprising:

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