Oil supply parts, compressors, and refrigeration cycle devices

Abstract

An oil feed component according to the present disclosure comprises: a main plate portion in which a through-hole is formed; and a plurality of insertion portions which project from positions on the main plate portion that are farther toward an outer circumferential portion side of the main plate portion than the through-hole, and which are inserted into oil feed holes in a rotating shaft of the compressor. Each insertion portion comprises a base end portion connected to the main plate portion, and a tip end portion on a tip end side of the insertion portion. Furthermore, if a virtual straight line which passes through the through-hole and is perpendicular to the main plate portion is defined as a first virtual straight line, in each insertion portion, a connecting portion, which is a connecting part of the base end portion and the insertion portion, is disposed in a position farthest from the first virtual straight line.

Description

[Technical field]

[0001] The present disclosure relates to an oil supply part that is provided in a compressor and improves the ability to supply refrigeration oil to sliding parts in a low rotation range, a compressor including the oil supply part, and a refrigeration cycle apparatus including the compressor. [Background technology]

[0002] Conventionally, a 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 lubricating oil, is sucked into the oil supply hole. The refrigeration oil sucked into the oil supply hole is then supplied to sliding parts such as a 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 a low rotation range (see Patent Document 1).

[0003] Specifically, Patent Document 1 discloses an oil supply part under the name of a suction member. The oil supply part disclosed in Patent Document 1 includes a flat main plate. A through hole is formed in the main plate. The main plate includes 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 disclosed in Patent Document 1 to the end of the rotating shaft on the side where the oil supply hole is open. In the 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 to 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. [Prior art documents] [Patent documents]

[0004] [Patent Document 1] Japanese Utility Model Application Publication No. 63-154787 Summary of the Invention [Problem to be solved by the invention]

[0005] 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 circumferential surface of the rotating shaft. Therefore, the lubrication part described in Patent Document 1 has a problem 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.

[0006] The present disclosure has been made to solve the above-mentioned problems, and has a first object to provide an oil supply part that can be attached to a rotating shaft of a compressor more easily than before. A second object of the present disclosure is to provide a compressor including such an oil supply part. A third object of the present disclosure is to provide a refrigeration cycle device including such a compressor. [Means for solving the problem]

[0007] 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, the oil supply part being provided in a compressor having 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 a through hole 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 hole and are inserted into the oil supply hole, and each of the insertion parts has a base end portion having a second end portion that is one end connected to the main plate portion, and a fourth end portion that is one end connected to a third end portion that is the other end of the base end portion. and a tip end portion, the other end of which is a fifth end, which is a tip end portion that becomes the tip of the insertion portion, 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 farthest from the first virtual line, and in each of the tip ends, the fourth end is disposed at a position farthest from the first virtual line, and each of the insertion portions is fixed to the rotation shaft by a connection portion that is a connection point between the third end of the base end portion and the fourth end of the tip end portion and that comes into contact with an inner circumferential surface of the rotation shaft. One of the insertion parts is formed by twisting a plate-shaped member and has a wing part connected to the fifth end part. It is composed of:

[0008] Moreover, 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 by 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 in which refrigeration oil is stored, 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 into the interior to the compression mechanism, each of the insertion parts of the oil supply part is inserted into the oil supply hole, each of the connection parts of the insertion parts contacts an inner circumferential surface of the rotating shaft, and the oil supply part is fixed to the rotating shaft.

[0009] 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. Effect of the Invention

[0010] In the lubrication part according to the present disclosure, when the lubrication part is fixed to the rotating shaft, the insertion parts are inserted into the lubrication holes of the rotating shaft while the outer surfaces of the connection parts of the insertion parts are in contact with the inner peripheral surface of the rotating shaft. Therefore, the lubrication part according to the present disclosure can reduce resistance when inserting the insertion parts into the lubrication holes of the rotating shaft compared to conventional methods. Therefore, the lubrication part according to the present disclosure can be attached to the rotating shaft of a compressor more easily than conventional methods. [Brief description of the drawings]

[0011] [Figure 1] 1 is a vertical cross-sectional view showing an overall configuration of a compressor according to a first embodiment. [Diagram 2] 1 is a diagram showing a refrigeration cycle device according to a first embodiment. [Diagram 3] 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. [Figure 4] FIG. 1 is a vertical cross-sectional view showing a fuel supply part according to a first embodiment. [Diagram 5] FIG. 2 is a plan view showing the fuel supply part according to the first embodiment. [Figure 6] 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. [Figure 7] FIG. 11 is a schematic diagram showing a fuel supply part according to a comparative example as viewed from the side. [Figure 8] FIG. 11 is a schematic diagram showing a fuel supply part according to a comparative example as viewed from the side. [Figure 9] FIG. 11 is a vertical cross-sectional view showing a fuel supply part according to a second embodiment. [Figure 10] FIG. 11 is a bottom view showing the fuel supply part according to the second embodiment. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0012] Embodiment 1 FIG. 1 is a vertical cross-sectional view showing an 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 the 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 by the compression mechanism 20 to the outside of the compressor shell 10 . The configuration of the compressor 1 will be described in detail below.

[0013] (Compressor housing 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.

[0014] A head portion 11 constituting an upper portion of the compressor shell 10 has, for example, a substantially bowl shape as shown in Fig. 1. A discharge pipe 4 that communicates between the inside and outside of the compressor shell 10 is connected to the head portion 11.

[0015] The body portion 12 constituting the middle portion of the compressor outer casing 10 has, for example, a substantially cylindrical shape as shown in Fig. 1. A first suction pipe 2A and a second suction pipe 2B for supplying a refrigerant into the compressor outer casing 10 are connected to the body portion 12. A stator 32 of a rotating electric machine 30 is attached to the inner circumferential surface of the body portion 12. A compression mechanism 20 is attached to the inner circumferential surface of the body portion 12. In the first embodiment, a rolling piston type compression mechanism is adopted as the compression mechanism 20. In such a case, the compression mechanism 20 is often attached to the inner circumferential surface of the body portion 12 below the position where the stator 32 is attached.

[0016] The bottom 13 constituting the lower part of the compressor outer casing 10 has, for example, a substantially bowl shape as shown in Fig. 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 and the like, thereby reducing friction at sliding parts of the compression mechanism 20 and the like.

[0017] (First suction pipe 2A and second suction 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.

[0018] (Intake muffler 3) The suction muffler 3 functions as a muffler that reduces refrigerant noise and the like that occurs 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.

[0019] (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 the cylinders. The first cylinder 21A is in communication with 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.

[0020] The first cylinder 21A is provided with a first piston 22A that rotates slidably within the first cylinder 21A. The first piston 22A is connected to the rotating shaft 40 so as to rotate eccentrically within the first cylinder 21A with respect to the center of rotation of the rotating shaft 40. Hereinafter, the rotational motion eccentric to the center of rotation of the rotating shaft 40 is referred to as eccentric rotational motion. The second cylinder 21B is provided with a second piston 22B that rotates slidably within the second cylinder 21B. The second piston 22B is connected to the rotating shaft 40 so as to rotate eccentrically within the second cylinder 21B.

[0021] Also, the first piston 22A is connected to the rotating shaft 40 so as to be able to rotate in the first cylinder 21A with a phase shift of 180 degrees with respect 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 as to be able to rotate in the second cylinder 21B with a phase shift of -180 degrees with respect to the rotation phase when the first piston 22A rotates in the first cylinder 21A.

[0022] 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. That is, 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.

[0023] The upper bearing 24A is provided with a valve (not shown) that discharges the refrigerant compressed by the first cylinder 21A and the first piston 22A. When this valve is opened, the space formed by the first cylinder 21A and the first piston 22A can be communicated with the first muffler 23A described below. The lower bearing 24B is provided with a valve (not shown) that discharges the refrigerant compressed by the second cylinder 21B and the second piston 22B. When this valve is opened, the space formed by the second cylinder 21B and the second piston 22B can be communicated with the second muffler 23B described below.

[0024] 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 to 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 via a refrigerant flow path (not shown). As a result, the refrigerant compressed by the second cylinder 21B and the second piston 22B is discharged to the second muffler 23B, and then flows into the first muffler 23A via a refrigerant flow path (not shown). The refrigerant that has flowed into the first muffler 23A is discharged into the compressor housing 10 from a refrigerant discharge portion of the first muffler 23A.

[0025] (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 a multi-phase winding on a laminated core.

[0026] 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 transmits the power of the rotating electric machine 30 to the compression mechanism 20. In the first embodiment, 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 about an axis extending in the vertical direction of the paper as a rotation center. 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 a portion rotatably supported by the upper bearing 24A and a portion rotatably supported by the lower bearing 24B of the rotating shaft 40 so that they can perform eccentric rotation. As a result, the rotating shaft 40 also rotates 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. That is, 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.

[0027] (Discharge piping 4) The discharge pipe 4 is a pipe that discharges the refrigerant compressed in the compression mechanism 20 to the outside of the compressor shell 10. That is, 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.

[0028] (Centrifugal Pump 45) The rotating shaft 40 is formed with 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 is also formed with 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 facing the compression mechanism 20 on the outer circumferential surface of the rotating shaft 40. In the first embodiment, the other end of first oil supply port 43 opens at a position facing upper bearing 24A of compression mechanism 20. Moreover, the other end of second oil supply port 44 opens at a position facing lower bearing 24B of compression mechanism 20.

[0029] 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-like member. The centrifugal pump 45 is a fluid machine that sucks up the refrigeration oil 6 as a lubricant oil stored in the bottom part 13 of the compressor outer shell 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.

[0030] [Operation of the 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.

[0031] [Flow of refrigerant] The refrigerant is drawn into the compressor 1 by the eccentric rotation of the first piston 22A and the second piston 22B. Specifically, the low-pressure refrigerant outside the compressor 1 flows into the suction muffler 3 by the eccentric rotation of the first piston 22A and the second piston 22B. 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 electrical machine 30 and the like, and is discharged from the discharge pipe 4.

[0032] The rest 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. Then, the high-temperature, high-pressure gaseous refrigerant sent into the first muffler 23A is discharged into the space inside the compressor outer shell 10 from a refrigerant discharge part (not shown) provided in the first muffler 23A. Then, the high-temperature, high-pressure gaseous refrigerant discharged into the space inside the compressor outer shell 10 moves to the upper part of the space inside the compressor outer shell 10 through gaps such as the rotating electric machine 30, and is discharged from the discharge pipe 4.

[0033] Furthermore, the refrigeration oil 6 stored in the bottom portion 13 within 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. Furthermore, the refrigeration oil 6 flows from the second oil supply port 44 into the space between the lower bearing 24B and the rotating shaft 40. The flow of the refrigeration oil 6 between these allows the rotating shaft 40 to smoothly transmit the rotational driving force to the first piston 22A and the second piston 22B.

[0034] Also, 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. Also, 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.

[0035] [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 radiates 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.

[0036] The refrigeration cycle apparatus 200 is used for various purposes such as a hot water supply apparatus and a refrigeration apparatus. FIG. 2 shows an example in which the refrigeration cycle apparatus 200 is used as an air conditioner. For this reason, the refrigeration cycle apparatus 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 apparatus 200 shown in FIG. 2 is also capable of cooling operation. For this reason, the refrigeration cycle apparatus 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 compressor 1 for the refrigerant, and switches the heat exchanger connected to the suction muffler 3, which is the suction port of the compressor 1 for the refrigerant. During cooling operation, the indoor heat exchanger 204 functions as an evaporator, and the outdoor heat exchanger 202 functions as a radiator.

[0037] When the refrigeration cycle apparatus 200 is used as an air conditioner, for example, the indoor heat exchanger 204 is mounted in an indoor device. Also, for example, the four-way switching valve 201, the outdoor heat exchanger 202, and the pressure reducer 203 are mounted in an outdoor device. Also, for example, the refrigeration cycle apparatus 200 uses R407C refrigerant, R410A refrigerant, R32 refrigerant, or the like. Hereinafter, the operation of the refrigeration cycle apparatus 200 during heating operation and cooling operation will be described.

[0038] When the refrigeration cycle device 200 performs heating operation, the four-way switching valve 201 is switched 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, the 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.

[0039] 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 reduced in pressure 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 and 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 heating operation, the refrigerant circulates as shown by the solid arrows in FIG. 2.

[0040] When the refrigeration cycle device 200 performs cooling operation, the four-way switching valve 201 switches to the flow path shown by the broken 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, the 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.

[0041] The high-pressure liquid refrigerant flowing out from the outdoor heat exchanger 202 flows into the pressure reducer 203. The high-pressure liquid refrigerant flowing into the pressure reducer 203 is reduced in pressure 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 indoor heat exchanger 204. The low-temperature, low-pressure two-phase gas-liquid refrigerant flowing into the indoor heat exchanger 204 absorbs heat from the indoor air and evaporates, and flows out from the indoor heat exchanger 204 as a low-pressure gaseous refrigerant or a two-phase gas-liquid refrigerant. At this time, the indoor air is cooled. The low-pressure gaseous refrigerant or two-phase gas-liquid refrigerant flowing out from 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 arrow in FIG. 2.

[0042] (100 oil supply parts) In compressor 1 according to the first embodiment, in order to improve the supply capacity of refrigeration oil 6 to the sliding parts of compression mechanism 20 when rotating shaft 40 is in the low rotation range, oil supply part 100 is attached to end part 41 of rotating shaft 40. Details of oil supply part 100 according to the first embodiment will be described below.

[0043] Fig. 3 is a vertical cross-sectional view showing a state in which the lubrication part 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 part according to the first embodiment. Fig. 5 is a plan view showing the lubrication part 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, and S50C.

[0044] As shown in Figs. 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 on the outer periphery 112 side of the main plate 110 relative to 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. More specifically, 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.

[0045] In the oil supply component 100 configured as described above, the through hole 111 is formed on the inner circumferential side 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, it is possible 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. That is, it is possible to ensure the reliability of the compressor 1 when the rotating shaft 40 is in the low rotation range.

[0046] Here, conventionally, there exists an oil supply part having a main plate part configured similarly to the main plate part 110 of the oil supply part 100 according to the present embodiment 1. This conventional oil supply part has a problem that it is difficult to attach it to the rotating shaft of the compressor. Therefore, in the oil supply part 100 according to the present embodiment 1, each of the insertion parts 120 is configured as follows.

[0047] Specifically, each of the insertion parts 120 includes a base end 121 and a tip end 125. The base end 121 has an end 122, which is one end, connected to the main plate part 110. This end 122 corresponds to the second end. An end 126, which is one end of the tip part 125, is connected to an end 123, which is the other end of the base end 121. Also, an end 127, which is the other end of the tip part 125, is the tip of the insertion part 120. The end 123 corresponds to the third end, the end 126 corresponds to the fourth end, and the end 127 corresponds to the fifth end. Hereinafter, the connection part between the end 123 of the base end 121 and the end 126 of the tip part 125 is referred to as a connection part 130.

[0048] Each of the insertion parts 120 thus configured 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 rotation center 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 way, 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 imaginary straight line L1.

[0049] 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.

[0050] Specifically, 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. A diameter of the oil supply hole 42 formed in the rotating shaft 40 is defined as a third diameter D3. In this definition, 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.

[0051] Below, the reason why the oil supply part 100 according to this embodiment 1 can be attached to the rotating shaft 40 easier than in the past will be explained based on a schematic diagram of the oil supply part 100 according to this embodiment 1 and a schematic diagram of an oil supply part according to a comparative example.

[0052] Fig. 6 is a schematic diagram showing a state in which the lubrication part according to the embodiment 1 is observed from the side. Figs. 7 and 8 are schematic diagrams showing a state in which the lubrication part according to the comparative example is observed from the side. Note that Figs. 6 to 8 illustrate a pair of opposing insertion parts.

[0053] 6, in each of the insertion parts 120 of the fuel supply part 100 according to the first embodiment, 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. Also, in each of the tip ends 125, the end 126 is disposed at a position farthest from the first virtual straight line L1.

[0054] In each of the insertion parts 320 of the lubrication part 300 according to the comparative example shown in Fig. 7, the base end 321 has the same distance from the first imaginary line L1 over the entire area. Also, the tip end 325 has the same distance from the first imaginary line L1 over the entire area. That is, in the lubrication part 300 according to the comparative example shown in Fig. 7, the insertion parts 320 extend parallel to the first imaginary line L1 from the main plate part 310. Also, each of the insertion parts 320 is parallel. The engagement claw of the lubrication part described in Japanese Utility Model Application Laid-Open Publication No. 63-154787, which is shown as a document disclosing the prior art, has the same shape as the insertion part 320 shown in Fig. 7.

[0055] In each of the insertion parts 420 of the fuel supply part 400 according to the comparative example shown in Fig. 8, the base end 421 has the same distance from the first imaginary line L1 over the entire area. Moreover, 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 Fig. 8, the base end 421 of the insertion part 420 extends from the main plate part 410 in parallel with the first imaginary line L1. Moreover, each of the base end parts 421 of the insertion parts 420 is parallel to each other.

[0056] When attaching the oil supply part to the rotating shaft, first, each of the inserting parts of the oil supply part is inserted into the oil supply hole of the rotating shaft so that the outer surface of each of the inserting parts of the oil supply part is in contact with the inner peripheral surface of the rotating shaft. Then, each of the inserting parts is inserted into the oil supply hole until the oil supply part is in a specified attachment position. Each of the inserting parts whose outer surface is in contact with the inner peripheral surface of the rotating shaft is pressed by the inner peripheral surface of the rotating shaft and deformed. Therefore, a spring force is generated in each of the inserting parts whose outer surface is in contact with the inner peripheral surface of the rotating shaft. The spring force of the inserting part is a reaction force generated in the inserting part when the deformed inserting part tries to return to its original shape. The oil supply part is fixed to the rotating shaft by the spring force of each of the inserting parts inserted into the oil supply hole of the rotating shaft. In this manner, the oil supply part is attached to the rotating shaft.

[0057] 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 parts 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 peripheral surface 46 of the rotating shaft 40 until the lubrication part 300 reaches a specified mounting position. Therefore, in the lubrication part 300 according to the comparative example shown in FIG. 7, the resistance when each of the insertion parts 320 is inserted into the lubrication hole 42 is large. Therefore, it is difficult to attach the lubrication part 300 according to the comparative example shown in FIG.

[0058] 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 parts 425 decreases from the base end part 421 side toward the tip part. 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 part 425 may be smaller than the third diameter D3 which is the diameter of the lubrication hole 42. This is because even if each tip part of the tip part 425 is disposed at such a position, when the insertion part 420 is inserted into the lubrication hole 42, each outer surface of the base end part 421 can contact the inner circumferential surface 46 of the rotating shaft 40. Therefore, in the lubrication part 400 according to the comparative example shown in FIG. 8, it is easier to insert each tip part of the insertion part 420 into the lubrication hole 42, compared with the lubrication part 300 according to the comparative example shown in FIG. 7.

[0059] 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 circumferential surface 46 of the rotating shaft 40 until the lubrication part 400 reaches a specified mounting position. Therefore, the lubrication part 400 according to the comparative example shown in FIG. 8 has a large resistance when each of the insertion parts 420 is inserted into the lubrication hole 42. Therefore, the lubrication part 400 according to the comparative example shown in FIG. 8 is also difficult to mount on the rotating shaft 40, similar to the lubrication part 300 according to the comparative example shown in FIG. 7.

[0060] On the other hand, in the lubrication part 100 according to the first embodiment, as described above, the second diameter D2 of the second imaginary 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, in the lubrication part 100 according to the first embodiment, it is 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 imaginary 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.

[0061] Furthermore, 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 is in contact with the inner circumferential surface 46 of the rotating shaft 40 until the lubrication part 100 reaches a specified mounting position. That is, each of the connection parts 130 of the insertion parts 120 is in contact with the inner circumferential surface 46 of the rotating shaft 40 and is fixed to the rotating shaft 40. Therefore, 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 mounted on the rotating shaft 40 more easily than before.

[0062] In the first embodiment, as shown in FIG. 4, the base end 121 and the tip end 125 are formed with inclined surfaces, so that each of the insertion sections 120 is configured 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 using the first inclined surface portion 124 and the second inclined surface portion 128 in this manner, the formation of the insertion portion 120 becomes simple, and the manufacture of the fuel supply part 100 becomes easy.

[0063] Furthermore, when the insertion part 120 is configured using the first inclined surface part 124 and the second inclined surface part 128, the angles of the first inclined surface part 124 and the second inclined surface part 128 are preferably set as follows. Preferred angles of the first inclined surface part 124 and the second inclined surface part 128 will be described below with reference to the schematic diagram of the fuel supply part 100 shown in FIG.

[0064] As shown in FIG. 6, a 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 a 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 circumferential 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 located at a position where the second diameter D2 is as small as possible so that the insertion into the oil supply hole 42 of the rotating shaft 40 is easily performed. Therefore, it is preferable that the angle β formed 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 formed between the second imaginary straight line L2 and the first inclined surface portion 124 of the base end portion 121.

[0065] 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 circumferential part 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 becomes easy to position the oil supply part 100 when attaching the oil supply part 100 to the rotating shaft 40. Also, by providing the contact part 140 to the oil supply part 100, it is possible to prevent the oil supply part 100 from entering inside the oil supply hole 42 while the compressor 1 is in operation. Therefore, by providing the oil supply component 100 with the contact portion 140, the reliability of the compressor 1 is improved.

[0066] The number of the insertion parts 120 provided in the refueling part 100 is not particularly limited as long as it is a plurality. 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.

[0067] As described above, the oil supply part 100 according to the first embodiment is provided in the compressor 1 having the rotating shaft 40 in which the oil supply hole 42 opening at the end 41 is formed and the refrigeration oil 6 sucked into the oil supply hole 42 is supplied to the compression mechanism 20. The oil supply part 100 includes a main plate portion 110 and a plurality of insertion portions 120. The main plate portion 110 is formed with a through hole 111. 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 includes 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 end portion 121, and the end portion 127 is the tip of the insertion portion 120. If a virtual line that passes through the through hole 111 and is perpendicular to the main plate portion 110 is defined as a first virtual line L1, then in each of the base ends 121, the end 123 is disposed at a position farthest from the first virtual line L1. Also, in each of the tip ends 125, the end 126 is disposed at a position farthest from the first virtual line L1. Then, in each of the insertion portions 120 of the fuel supply part 100, a connection portion 130 that is a connection portion between the end 123 of the base end 121 and the end 126 of the tip end 125 comes into contact with the inner circumferential surface 46 of the rotating shaft 40, and is fixed to the rotating shaft 40.

[0068] As described above, the lubrication part 100 configured in this manner makes it easy to insert each of the ends 127, which are the tips of the insertion parts 120, into the lubrication hole 42. Furthermore, as described above, the lubrication part 100 configured in this manner can reduce the resistance when each of the insertion parts 120 is inserted into the lubrication hole 42. Therefore, the lubrication part 100 configured in this manner can be attached to the rotating shaft 40 more easily than before.

[0069] 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. Note that 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.

[0070] 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 wing part 145 which is formed by twisting a plate-like member and connected to an end part 127 of a tip part 125. - Stacks of blades 145 are provided in the insertion parts 120.

[0071] Specifically, the third imaginary line L3 shown in FIG. 9 and FIG. 10 indicates the position that becomes 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 part 145, which is a plate-like member, is observed from the end part on the end part 127 side of the insertion part 120 to the end part on the opposite side of the end part. In this case, the blade part 145 extends from one end part 127 of the insertion part 120 toward the third imaginary line L3. Also, it bends at the position of the third imaginary line L3, and then extends along the third imaginary line L3. The blade part 145, which is a plate-like member, is twisted at the part that extends along the third imaginary line L3. When the oil supply part 100 is attached to the rotating shaft 40, the twisted part of the blade part 145 is disposed inside the oil supply hole 42, and functions as a centrifugal pump.

[0072] That is, the lubrication part 100 according to the second embodiment has a configuration in which the centrifugal pump is integrally formed. Therefore, the compressor 1 in which the lubrication part 100 according to the second embodiment is provided does not require the centrifugal pump 45 shown in the first embodiment. Therefore, by adopting the lubrication part 100 according to the second embodiment, the number of parts of the compressor 1 can be reduced. Furthermore, by attaching the lubrication 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 lubrication part 100 according to the second embodiment, the number of assembly steps of the compressor 1 can also be reduced. [Explanation of symbols]

[0073] 1 compressor, 2A first suction pipe, 2B second suction pipe, 3 suction muffler, 4 discharge piping, 6 refrigeration oil, 10 compressor outer shell, 11 head, 12 body portion, 13 bottom portion, 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 portion, 42 oil supply hole, 43 first oil supply port, 44 second oil supply port, 45 centrifugal pump, 46 inner peripheral surface, 100 oil supply part, 110 main plate portion, 111 through hole, 112 outer peripheral portion, 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 2nd diameter, D3 3rd diameter, L1 1st imaginary line, L2 2nd imaginary line, L3 3rd imaginary line.

Claims

1. 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.

2. 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.

3. 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; The lubrication part according to claim 1 or 2.

4. 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.

5. 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.

6. 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.

7. 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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