CZ2024210A3 - A component for oil supply, a compressor and a cooling cycle equipment - Google Patents

Abstract

An oil supply component (100) according to the present disclosure includes: a main plate portion (110) on which a through hole (111) is formed; and a plurality of plug-in portions (120) each protruding from the main plate portion (110) at a position near an outer peripheral portion (112) of the main plate portion (110) relative to the through hole (111), wherein the plurality of plug-in portions are ( 120) inserted into the oil supply hole (42) in the rotating shaft (40) of the compressor (1). Each of the plug parts (120) includes a base end part (121) connected to the main plate part (110) and a top end part (125) on the top end side of the plug part (120). In the case where the imaginary straight line passing through the through hole (111) and perpendicular to the main plate part (110) is defined as the first imaginary straight line (L1), in each of the plug-in parts (120), the connecting part (130) which is a place, where the base end part (121) and the plug part (120) are connected, is located at the position farthest from the first imaginary line (L1).

Description

Field of technology

[0001] The proposed disclosure relates to an oil supply component arranged in a compressor for the purpose of improving the ability of a refrigerating machine to supply oil to sliding elements in the range of low revolutions, thereby also to a compressor containing this oil supply component, and a refrigeration cycle device containing this compressor.

Current state of the art

[0002] Patent literature 1: Published Japanese utility model c. JP S63154787 U

[0003] In a running compressor, the oil supply hole is formed in the rotary shaft of the compressor and is opened at one end part of the rotary shaft. When the rotary shaft rotates, the oil of the cooling machine is sucked into the oil supply hole, which serves as lubricating oil. The oil of the refrigerating machine sucked into the oil supply hole is supplied to the sliding elements of the compression mechanism and other machines. Another conventional compressor has also been designed in which the oil supply component is arranged at the end of the rotary shaft in which the oil supply port is opened, thereby designed to improve the ability of the refrigerating machine to supply oil to the sliding elements in a condition where rotating shafts fall into the range of low speeds (see patent literature 1).

[0004] Patent Literature 1 specifically discloses an oil supply component which is referred to as a "suction element". The oil supply component described in patent literature 1 contains a main plate part in the shape of a flat plate. A through hole is created on the main plate part. The main plate part is provided with a plurality of retaining elements, each of which protrudes from the main plate part in a position close to its outer peripheral part in relation to the through hole. A plurality of retaining members are inserted into the oil supply hole in the rotary shaft, and the outer surfaces of the plurality of retaining members are brought into contact with the inner peripheral surface of the rotary shaft, so that the oil supply component described in Patent Literature 1 is attached to the end portion of the rotary shaft, in which the oil supply hole is open. In the oil supply component with the configuration described above, a through hole is formed on the inner peripheral side in relation to a plurality of receiving units to be inserted into the oil supply hole. Thanks to this design, the through hole has a smaller diameter than the diameter of the oil supply hole in the rotary shaft. As already described above, the oil supply component has such a configuration that allows the oil of the cooling machine to be sucked into the oil supply hole in the rotary shaft from a through hole with a diameter smaller than the diameter of the oil supply hole in the rotary shaft. Thus, the oil supply component can improve the ability of the cooling machine to supply oil to the sliding elements in a condition where the rotating shaft falls into the low speed range.

The essence of the invention

In the oil supply component described in Patent Literature 1, each of the retaining members extends directly in the axial direction of the rotating shaft, in other words, in the direction in which the oil supply hole is formed. Due to this construction, in the oil supply component described in patent literature 1, at the time of fixing the oil supply component to the rotary shaft, the catch unit is inserted into the oil supply hole in the rotary shaft, while the main part of the outer surface of each of the catch units is in contact with the inner peripheral surface of the rotary shaft. This leads to the problem that it is difficult to connect the oil supply component described in Patent Literature 1 to the rotary shaft of the compressor due to the increase in resistance caused by the insertion of the catch elements into the oil supply hole in the rotary shaft.

[0006] The proposed publication was created to solve all of the above problems and first

- 1 CZ 2024 - 210 A3 the aim of the present disclosure is to provide an oil supply component which is connected to the rotary shaft of the compressor more easily than is the case with a conventional oil supply component. A second objective of the present disclosure is to provide a compressor comprising the above-described oil supply component. A third object of the present disclosure is to provide a refrigeration cycle device comprising the compressor described above.

The oil supply component according to one of the embodiments of the present disclosure is an oil supply component arranged in a compressor containing a rotary shaft, in which an oil supply hole is formed to supply the oil of the refrigerating machine sucked into the oil supply hole to the compression mechanism, through this oil supply hole is opened in the first end part, the first end part is one end part of the rotary shaft, whereby the oil supply component includes: a main plate part on which a through hole is formed; and a plurality of plug-in parts, each of which protrudes from the main plate part in a position near the outer peripheral part of the main plate part in relation to the passage of the hole, whereby the plurality of plug-in parts is inserted into the oil supply hole, where each of the plug parts includes a base end part connected with the main plate part at the second end part, through which the second end part is one end part of the base end part, and the top end part connected to the third end part at the fourth end part, through the third end part is another end part of the base end part, the fourth end The part is one end part of the top end part, the top end part is the fifth end part, this fifth end part is another end part of the top end part, and the fifth end part is the top end of the plug-in part, where the imaginary straight line passing through the through hole and perpendicular to the main plate part, is defined as the first imaginary line, in each of the base end parts, this third end part is located in the position farthest from the first imaginary line, and in each of the vertex end parts, the fourth end part is located in the position farthest from the first imaginary line , and in each of the plug-in parts, the coupling part is in contact with the inner peripheral surface of the rotary shaft, whereby the oil supply component is fixed to the rotary shaft, and the coupling part is where the third end part of the base end part and the fourth end part are connected top end parts.

[0008] The compressor according to another embodiment of the present disclosure comprises: a rotary electric machine; rotating shafts connected to a rotating electric machine for the purpose of its rotation by means of the power of the rotating electric machine; a compression mechanism connected to the rotary shaft and configured to compress the refrigerant drawn in from the outside by means of the power of a rotary electric machine transmitted through the rotary shaft; the outer shell of the compressor, inside which the oil from the refrigerating machine is captured, whereby the rotating electric machine, rotating shafts and compression mechanism are stored inside this outer shell of the compressor; and an oil supply component according to one embodiment of the present disclosure, where an oil supply hole is formed and opened on the rotary shaft at one end part of the rotary shaft for supplying the oil of the refrigerating machine sucked in through the oil supply hole to the compression mechanism, through each of the plug-in parts the oil supply component is inserted into the oil supply hole, the connecting part of each of the plug parts is in contact with the inner peripheral surface of the rotary shaft, thereby the oil supply component is fixed to the rotary shaft.

A refrigeration cycle device according to yet another embodiment of the present disclosure comprises: a compressor according to another embodiment of the present disclosure; cooler, through which the heat of the refrigerant compressed by the compressor is transferred; a pressure reducing device configured to reduce the pressure of the coolant flowing out of the cooler; and the evaporator, which is used to evaporate the coolant in the stream from the device for reducing the pressure.

[0010] In the oil supply component according to one embodiment of the present disclosure, at the time of fixing this oil supply component to the rotary shaft, each of the plug-in parts is inserted into the oil supply hole in the rotary shaft, while the outer surface of the connecting part of each of the plug-in parts is in contact with the inner peripheral surface of the rotary shaft. Using this configuration, the drive component can be compared to a conventional oil supply component

- 2 CZ 2024 - 210 A3 oil according to one of the implementations of the proposed publication to reduce the resistance produced by inserting each of the plug-in parts into the oil supply hole in the rotating shaft. Therefore, the connection of the oil supply component according to one of the embodiments of the present disclosure to the rotary shaft of the compressor is easier than with a conventional oil supply component.

Clarification of the drawing

[0011]

Giant. 1 is a vertical sectional view showing the overall configuration of the compressor according to embodiment 1.

Giant. 2 shows the refrigeration cycle device according to embodiment 1.

Giant. 3 is a vertical sectional view showing the oil supply component of embodiment 1 connected to the end portion of the compressor rotary shaft.

Giant. 4 is a vertical sectional view showing the oil supply component according to embodiment 1.

Giant. 5 is a top view showing the oil supply component according to embodiment 1.

Giant. 6 is a schematic view showing the oil supply component according to embodiment 1 in side view.

Giant. 7 is a schematic illustration showing a component for supplying oil according to a comparative example in a side view.

Giant. 8 is a schematic side view showing the oil supply component according to the comparative example.

Giant. 9 is a vertical sectional view showing the oil supply component according to embodiment 2.

Giant. 10 is a bottom view showing the oil supply component according to embodiment 2.

Examples of the implementation of the invention

Done 1

Fig. 1 is a vertical sectional view showing the overall configuration of the compressor according to embodiment 1.

[Compressor 1 configuration]

As shown in Fig. 1, the compressor 1 according to embodiment 1, which is a rolling piston compressor, is shown as an example of the compressor according to the present disclosure. The compressor 1 contains the outer shell 10 of the compressor, the first suction pipe 2A, the second suction pipe 2B, the shock absorber 3, the compression mechanism 20, the rotating electric machine 30, the rotating shaft 40 and the discharge pipe 4. The outer shell 10 of the compressor forms the outer shell of the compressor 1. Refrigerant is brought inside the outer layer 10 of the compressor via the first suction pipe 2A and the second suction pipe 2B. The muffler 3 is connected to the first intake pipe 2A and the second intake pipe 2B. The compression mechanism 20 is connected to the first suction pipe 2A and the second suction pipe 2B and is configured to compress the refrigerant. The rotating electric machine 30 contains a rotor 31 and a stator 32. The rotating shaft 40 is connected to the rotor 31 of the rotating electric machine 30 so that it rotates together with the rotor 31. Through the discharge pipe 4, the refrigerant compressed in the compression mechanism 20 is pushed to the outside of the outer shell 10 compressor.

- 3 CZ 2024 - 210 A3

The configuration of Compressor 1 is detailed below.

[0013] (External surface 10 of the compressor)

The outer shell 10 of the compressor forms the outer shell of the compressor 1 and the compression mechanism 20, rotating electric machine 30, rotating shafts 40 and other elements are stored in it. The outer layer 10 of the compressor includes the upper part 11, the lower part 13 and the body part 12. The upper part 11 forms the outer layer of the upper part of the compressor 1. The lower part 13 forms the outer layer of the lower part of the compressor 1. The body part 12 forms the outer layer of the central part of the compressor 1. The upper part 11 is connected to the top of the body part 12, while the lower part 13 is connected to the bottom of the body part 12.

[0014] The upper part 11, which forms the upper part of the outer layer 10 of the compressor, has, for example, a basically bowl-shaped shape, as shown in Fig. 1. The discharge pipe 4, which is the inside of the outer layer 10 of the compressor, is connected to the upper part 11 connected to the outside of the outer layer 10 of the compressor.

[0015] The body part 12, which forms the middle part of the outer layer 10 of the compressor, has, for example, a substantially cylindrical shape, as shown in Fig. 1. The first suction pipe 2A and the second suction pipe 2B, which are inside the outer layer 10 of the compressor supplied refrigerant, are connected to the body part 12. The stator 32 of the rotating electric machine 30 is installed on the inner peripheral surface of the body part 12. The compression mechanism 20 is installed on the inner peripheral surface of the body part 12. In the present embodiment 1, the compression mechanism 20 is used mechanism with a rolling piston. In this case, the compression mechanism 20 is installed on the inner peripheral surface of the body part 12, often on the underside of the position where the stator 32 is installed.

[0016] The lower part 13, which forms the lower part of the outer layer 10 of the compressor, has, for example, a basically bowl-shaped shape, as shown in Fig. 1. In the lower part 13, the oil 6 of the refrigerating machine serving as lubricating oil is captured. This means that the oil 6 of the refrigerating machine is trapped in the outer casing 10 of the compressor. The oil 6 of the cooling machine is supplied to the compression mechanism 20 and other machines for the purpose of reducing friction between the sliding elements of the compression mechanism 20 and other machines.

(First suction pipe 2A and second suction pipe 2B)

As already described above, the first suction pipe 2A and the second suction pipe 2B are connected to the body part 12 of the outer layer 10 of the compressor. One end part of the first suction pipe 2A is connected to the first cylinder 21A of the compression mechanism 20. The first cylinder 21A will be described below. The other end part of the first intake pipe 2A is connected to the muffler 3. One end part of the second suction pipe 2B is connected to the second cylinder 21B of the compression mechanism 20. The second cylinder 21B will be described below. The other end part of the second intake pipe 2B is connected to the muffler 3.

[0018] (Shuffler 3 sàni)

Muffler 3 serves as a muffler configured to dampen the noise of the refrigerant or other sounds generated by the refrigerant flowing into compressor 1. Muffler 3 also serves as an accumulator that is capable of capturing liquid refrigerant. The exhaust muffler 3 is connected to the first intake pipe 2A and the second intake pipe 2B, as described above.

(Compression Mechanism 20)

The compression mechanism 20 is connected to the rotating shaft 40 and is configured to compress the coolant sucked in from the outside by means of the power of the rotating electric machine 30 transmitted through the rotating shaft 40. In the present embodiment 1, the coolant flowing into the damper 3 of the sled is supplied through the first suction pipe 2A and the second suction pipe 2B into the compression mechanism 20. This means that the compression mechanism 20 sucks in refrigerant from the outside through the first suction pipe 2A and the second suction pipe 2B and compresses this refrigerant.

- 4 CZ 2024 - 210 A3

The refrigerant compressed in the compression mechanism 20 is sent to the inside of the outer layer 10 of the compressor. As already described above, in the preferred embodiment 1, a compression mechanism with a rolling piston is used as the compression mechanism 20. Based on this, the compression mechanism 20 includes a cylinder configured to compress the coolant sucked in from the outside. In the present embodiment 1, the compression mechanism 20 includes, as a roller, a first roller 21A and a second roller 21B. The first cylinder 21A is connected to the first suction pipe 2A and is configured to compress the refrigerant supplied from the first suction pipe 2A. The second cylinder 21B is connected to the second suction pipe 2B and is configured to compress the refrigerant supplied from the second suction pipe 2B.

[0020] The first cylinder 21A is provided with a first piston 22A, which slides and rotates inside the first cylinder 21A. The first piston 22A is connected to the rotary pin 40 so that it is able to perform a rotary movement in the first cylinder 21A eccentrically with respect to the rotation center of the rotary pin 40. The rotary movement eccentric with respect to the rotation center of the rotary pin 40 is referred to below as "eccentric rotary movement". The second cylinder 21B is covered with a second piston 22B, which rotates slidingly inside the second cylinder 21B. The second piston 22B is connected to the rotary pin 40 so that it is able to perform an eccentric rotary movement inside the second cylinder 21B.

The first piston 22A is connected to the rotary shaft 40 so that it can rotate in the first cylinder 21A with a phase shift of 180 degrees from the phase of rotation of the second piston 22B, which rotates inside the second cylinder 21B. In other words, the second piston 22B is connected to the pivot shaft 40 so that it can rotate in the second cylinder 21B with a phase shift of -180 degrees from the phase of rotation of the first piston 22A, which rotates inside the first cylinder 21A.

On the upper side of the first cylinder 21A, there is an upper bearing 24A arranged to support the rotary pin 40 in a rotatable manner. The upper bearing 24A closes the upper side opening of the first cylinder 21A. A separating plate 25 is provided on the lower side of the first roller 21A. The separating plate 25 closes the opening on the lower side of the first roller 21A, thereby also closing the opening on the upper side of the second roller 21B. This means that 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, on the lower side of the second cylinder 21B, a lower bearing 24B is arranged to support the rotary pin 40 in a rotary manner. The lower bearing 24B closes the lower side opening of the second cylinder 21B.

[0023] It should be noted that a valve (not shown) is arranged on the upper bearing 24A, through which the coolant compressed by the first cylinder 21A and the first piston 22A is sent. This valve is opened, which allows the space formed by the first cylinder 21A and the first piston 22A to be connected to the first damper 23A, which will be described later. A valve (not shown) is arranged on the lower bearing 24B, through which the coolant compressed by the second cylinder 21B and the second piston 22B is sent. This valve is open, which allows the space created by the second cylinder 21B and the second piston 22B to be connected to the second damper 23B, which will be described below.

A first damper 23A is provided on the upper bearing 24A, into which the coolant compressed by the first cylinder 21A and the first piston 22A is forced out. It should be noted that the first damper 23A is equipped with a part for pushing out the coolant (not shown). Based on this design, the refrigerant compressed by the first cylinder 21A and the first piston 22A is pushed into the first damper 23A and then sent to the inside of the outer layer 10 of the compressor from the part for pushing out the refrigerant. A second damper 23B is arranged on the lower bearing 24B, into which the coolant compressed by the second cylinder 21B and the second piston 22B is forced out. It should be noted that the second damper 23B is connected to the first damper 23A by a coolant flow channel (not shown). Based on this design, the coolant compressed by the second cylinder 21B and the second piston 22B is forced into the second damper 23B and then flows into the first damper 23A through the coolant flow channel (not shown). The refrigerant flowing into the first damper 23A is then sent from the refrigerant discharge part of the first damper 23A to the inside of the outer layer 10 of the compressor.

- 5 CZ 2024 - 210 A3

[0025] (Rotating electric machine 30 and rotating shafts 40)

The rotary electric machine 30 includes a rotor 31, which is configured to transmit its own revolutions to the rotary spindle 40, and a stator 32 made of multi-phase windings wound on a layered core.

The rotating spindle 40 is connected to the rotating electric machine 30 and rotates with the power of the rotating electric machine 30. Through the rotating shaft 40, the power of the rotating electric machine 30 is transferred to the compression mechanism 20. In the present embodiment 1, the rotating shaft 40 is on its top on the end side is connected to the rotor 31 of the rotating electric machine 30. This enables the rotating shaft 40 to rotate when the rotor 31 is rotated. It should be noted that the rotating shaft 40 shown in Fig. 1 rotates around an axis which, in the drawing in Fig. 1, extends in up-down direction. The rotary shaft 40 is connected to the compression mechanism 20 on its lower end side. More specifically, the rotary shaft 40 is rotatably supported on its lower end side by the upper bearing 24A and the lower bearing 24B of the compression mechanism 20. Between the place where the rotary shaft 40 is rotatably supported the upper bearing 24A, and the place where the rotary shaft 40 is rotatably supported by the lower bearing 24B, the first piston 22A and the second piston 22B are connected to the rotary shaft 40 so as to be able to perform an eccentric rotary movement. Based on this design, the rotary shaft 40 rotates when the rotor 31 rotates, while the first piston 22A and the second piston 22B perform an eccentric rotary movement. The coolant is compressed by the first cylinder 21A and the first piston 22A, thereby the coolant is also compressed by the second cylinder 21B and the second piston 22B. This means that the compression mechanism 20 compresses the refrigerant sucked in from the outside by means of the power of the rotary electric machine 30, which is transmitted by means of the rotary shaft 40.

[0027] (Discharge pipe 4)

Through the discharge pipe 4, the refrigerant compressed in the compression mechanism 20 is pushed to the outside of the outer shell 10 of the compressor. This means that high-pressure and high-temperature coolant in the outer shell 10 of the compressor is pushed out through the discharge pipe 4 to the outside of the outer shell 10 of the compressor.

(Centrifugal pump 45)

In the rotating shaft 40, an opening 42 for oil supply is formed and opened on the end part 41, which is one end part of the rotating shaft 40. End part 41 is identical to the first end part. In the proposed embodiment 1, the end part 41 is the lower end part of the rotary shaft 40. The oil supply hole 42 extends along the rotation center of the rotary shaft 40. The first oil supply port 43 and the second oil supply port 44 are further formed in the rotary shaft 40. The first oil supply port 43 and the second oil supply port 44 serve as a flow channel through which the oil 6 of the cooling machine sucked into the oil supply hole 42 is supplied to the sliding elements of the compression mechanism 20. One end part of the first oil supply port 43 and one The ends of the second oil supply port 44 are connected to the oil supply hole 42. The other end part of the first oil supply port 43 and the other end part of the second oil supply port 44 are opened on the outer peripheral surface of the rotary shaft 40 in the place attached to the compression mechanism 20. It should be noted that in the present embodiment 1, the other end part of the first of the oil supply port 43 is opened at a place attached to the upper bearing 24A of the compression mechanism 20. Another end part of the second oil supply port 44 is opened at a place attached to the lower bearing 24B of the compression mechanism 20.

The centrifugal pump 45 is arranged in the oil supply hole 42 in the rotary shaft 40. The centrifugal pump 45 is formed by twisting the plate-like element. The centrifugal pump 45 is a fluid machine configured to pump the oil 6 of the refrigerating machine trapped in the lower part 13 of the outer shell 10 of the compressor with the help of the centrifugal force generated by the rotary movement of the rotary shaft 40 so that it serves as lubricating oil. The oil 6 of the cooling machine pumped into the oil supply hole 42 by the centrifugal pump 45 is supplied to the sliding elements of the compression mechanism 20. Part of the oil 6 of the cooling machine pumped into the oil supply hole 42 specifically passes through the first oil supply port 43 and is supplied to the sliding elements between the upper bearing 24A of the compression mechanism 20 and the rotary shaft 40. Part of the oil 6 of the cooling machine pumped into

- 6 CZ 2024 - 210 A3 of the oil supply port 42 then passes through the second oil supply port 44 and is fed to the sliding elements between the lower bearing 24B of the compression mechanism 20 and the rotating shaft 40. Examples of used oil 6 of the cooling machine include mineral-based lubricating oils oils, based on alkylbenzene, based on polyalkylene glycol, based on polyvinyl ether and based on polyolester.

[0030] [Operation of rotary electric machine 30]

An electric current is supplied from a power source (not shown) to the windings arranged on the layered core of the stator 32 in order to create a rotating magnetic field in the stator 32. This is caused by the rotating magnetic field in the stator 32 acting on the permanent magnets arranged in the rotor 31, so the rotor 31 rotates. The rotation of the rotor 31 is transmitted via the rotary shaft 40 to the first piston 22A and the second piston 22B so as to cause the eccentric rotary movement of the first piston 22A and the second piston 22B.

[0031] [Coolant Flow]

If the first piston 22A and the second piston 22B perform an eccentric rotary movement, the refrigerant is sucked into the compressor 1. If the first piston 22A and the second piston 22B perform an eccentric rotary movement, the low-pressure refrigerant specifically flows from the outside of the compressor 1 into the damper 3. The low-pressure refrigerant in the gaseous state occupied in the low-pressure refrigerant flowing into the damper 3 flows into the compression mechanism 20 in the compressor 1 through the first suction pipe 2A and the second suction pipe 2B. A portion of the gaseous refrigerant that has flowed into the compression mechanism 20 is compressed by the first cylinder 21A and the first piston 22A into a high-temperature, high-pressure gaseous refrigerant. This high-temperature, high-pressure refrigerant in gaseous form flows into the first damper 23A through the valve on the upper bearing 24A. The high-temperature, high-pressure gas refrigerant that has flowed into the first damper 23A is sent from the refrigerant discharge part (not shown) arranged on the first damper 23A to the space in the outer casing 10 of the compressor. The high-temperature, high-pressure refrigerant in the gaseous state, which was sent to the space in the outer shell 10 of the compressor, then moves to the upper part of the space in the outer shell 10 of the compressor through the gap, etc. of the rotating electric machine 30 and is pushed out by the discharge pipe 4.

The remaining gas refrigerant that flowed into the compression mechanism 20 is compressed by the second cylinder 21B and the second piston 22B into a high-temperature, high-pressure gas refrigerant. This high-temperature, high-pressure gas refrigerant flows into the second damper 23B through the valve on the lower bearing 24B. The high-temperature, high-pressure refrigerant in the gaseous state that has flowed into the second damper 23B is supplied from the second damper 23B through the refrigerant flow channel (not shown) to the first damper 23A. The high-temperature, high-pressure gas refrigerant that has been supplied to the first damper 23A is sent from the refrigerant discharge part (not shown) arranged on the first damper 23A to the space in the outer casing 10 of the compressor. The high-temperature, high-pressure refrigerant in the gaseous state, which was sent to the space in the outer shell 10 of the compressor, then moves to the upper part of the space in the outer shell 10 of the compressor through the gap, etc. of the rotating electric machine 30 and is pushed out by the discharge pipe 4.

The oil 6 of the refrigerating machine trapped in the lower part 13 of the outer layer 10 of the compressor is pumped from the lower end part of the hole 42 for the oil supply by means of the centrifugal pump 45 rotating with the rotating shaft 40. The oil 6 of the refrigerating machine is pumped from the lower end part of the opening 42 to supply oil to serve as lubricating oil, flows into the gap between the upper bearing 24A and the rotating shaft 40 through the first oil supply port 43. The oil 6 of the cooling machine also flows into the gap between the lower bearing 24B and the rotating shaft 40 through the second oil supply port 44. The oil 6 of the cooling machine flows into these gaps, which can help to smoothly transmit the rotary driving force to the first piston 22A and the second piston 22B through the rotary shaft 40.

[0034] Part of the oil 6 of the refrigerating machine, which flowed into the gap between the upper bearing 24A and the rotary shaft 40 through the first oil supply port 43, flows into the gap between the upper bearing 24A and the upper surface of the first piston 22A. Part of the oil 6 of the cooling machine that flowed into the gap

- 7 CZ 2024 - 210 A3 between the lower bearing 24B and the rotating shaft 40 through the second port 44 for oil supply, then flows into the gap between the lower bearing 24B and the lower surface of the second piston 22B. Oil 6 of the cooling machine will help the first piston 22A and the second piston 22B rotate smoothly. However, part of the oil 6 of the refrigerating machine is compressed together with the low-pressure refrigerant in the gaseous state and is thus occupied by the high-temperature, high-pressure refrigerant in the gaseous state and subsequently pushed out.

[0035] [Configuration and Operation of Refrigerant Cycle 200] FIG. 2 shows the refrigeration cycle device according to embodiment 1.

The refrigeration cycle device 200 includes a compressor 1 according to the proposed embodiment 1, a cooler through which the refrigerant compressed by the compressor 1 transfers heat, a device 203 for reducing pressure, such as an electric expansion valve configured to reduce the pressure of the refrigerant flowing out of the refrigerator, and an evaporator through which the vaporized refrigerant flows out of the pressure reduction device 203.

[0036] The cooling cycle device 200 is used for various applications, such as hot water supply and device cooling. Giant. 2 shows an example in which a 200 refrigeration cycle device is used as an air conditioning device. Based on this, the refrigeration cycle device 200 shown in Fig. 2 includes a heat exchanger 204 on the inside serving as a cooler in the heating mode, and a heat exchanger 202 on the outside serving as an evaporator in the heating mode. The refrigeration cycle device 200 shown in Fig. 2 is also capable of operating in a cooling mode. Therefore, the refrigerant cycle device 200 includes a four-way switching valve 201. The four-way switching valve 201 is configured to switch each heat exchanger between the connection to the discharge pipe 4, which is the discharge port for the refrigerant of the compressor 1, and the connection to the damper 3, which is the suction compressor refrigerant port 1. During the cooling mode, heat exchanger 204 on the inside serves as an evaporator, while heat exchanger 202 on the outside serves as a cooler.

[0037] If the refrigeration cycle device 200 is used as an air conditioning device, the heat exchanger 204 on the inside is installed, for example, in the indoor device. The four-way switching valve 201, the heat exchanger 202 on the outdoor side and the device 203 for reducing the pressure are installed, for example, in the outdoor equipment. Examples of refrigerants for use in the 200 refrigerant cycle device include R407C refrigerant, R410A refrigerant, and R32 refrigerant.

Operation of the 200 cooling cycle device during heating mode and cooling mode is described below.

[0038] If the refrigeration cycle device 200 operates in the heating mode, the four-way switching valve 201 switches the flow channel to the flow channel shown in Fig. 2 by solid lines. In this switching operation, the discharge pipe 4 of the compressor 1 is connected to the heat exchanger 204 on the inside, while the damper 3 of the compressor 1 is connected to the heat exchanger 202 on the outside. This means that the heat exchanger 204 on the inner side and the heat exchanger 202 on the outer side are brought to a state in which the heat exchanger 204 on the inner side and the heat exchanger 202 on the outer side respectively serve as a cooler and an evaporator. In this state, the high-temperature, high-pressure gas refrigerant compressed by the compressor 1 is discharged from the compressor 1, and accordingly, this high-temperature, high-pressure gas refrigerant flows into the heat exchanger 204 on the inside. The high-temperature, high-pressure gas refrigerant that flows into the heat exchanger 204 on the inside condenses during heat transfer to the air in the room to the high-pressure liquid refrigerant that flows out of the heat exchanger 204 on the inside. At this time, the air in the room is heated. It should be noted that there are some types of refrigerants, containing refrigerants with carbon dioxide, which do not condense during heat transfer. In the case of using a coolant that condenses during heat transfer, the coolant can be designated as a condenser.

[0039] The high-pressure liquid refrigerant that flowed out of the heat exchanger 204 on the inner side flows into the pressure reduction device 203. The pressure of the high-pressure liquid refrigerant that has flowed into the pressure-reducing device 203 is reduced to a low-temperature, low-pressure two-phase gas-liquid refrigerant by the pressure-reducing device 203, and then

- 8 CZ 2024 - 210 A3 flows out of the pressure reduction device 203. The low-temperature, low-pressure gas-liquid two-phase refrigerant that flowed out of the pressure reduction device 203 flows into the heat exchanger 202 on the outside. The low-temperature, low-pressure two-phase gas-liquid refrigerant that has flowed into the heat exchanger 202 on the outside receives heat from the outside air and evaporates, and then flows out of the heat exchanger 202 on the outside as a low-pressure gas refrigerant or two-phase gas-liquid refrigerant . The low-pressure gas refrigerant or the two-phase gas-liquid refrigerant that flowed out of the heat exchanger 202 on the outside is sucked into the damper 3 of the compressor sled 1. The low-pressure gas refrigerant occupied by the refrigerant sucked into the damper 3 of the compressor 1 is compressed by compression mechanism 20 in compressor 1 to high-temperature, high-pressure refrigerant in gaseous state. The high-temperature, high-pressure refrigerant in the gaseous state is again forced out of the compressor 1. This means that if the 200 refrigerant cycle device operates in the heating mode, the refrigerant circulates in the manner shown by the solid arrows in Fig. 2.

[0040] If the refrigeration cycle device 200 operates in the cooling mode, the four-way switching valve 201 switches the flow channel to the flow channel shown in Fig. 2 by dotted lines. In this switching operation, the discharge pipe 4 of the compressor 1 is connected to the heat exchanger 202 on the outside, while the damper 3 of the compressor 1 is connected to the heat exchanger 204 on the inside. This means that the heat exchanger 202 on the outer side and the heat exchanger 204 on the inner side are thereby brought to a state in which the heat exchanger 202 on the outer side and the heat exchanger 204 on the inner side respectively serve as a cooler and an evaporator. In this state, the high-temperature, high-pressure gas refrigerant compressed by the compressor 1 is discharged from the compressor 1, and accordingly, this high-temperature, high-pressure gas refrigerant flows into the heat exchanger 202 on the outside. The high-temperature, high-pressure gas refrigerant that flowed into the heat exchanger 202 on the outside condenses during heat transfer to the outside air to the high-pressure liquid refrigerant that flows out of the heat exchanger 202 on the outside.

[0041] The high-pressure liquid refrigerant that flowed out of the heat exchanger 202 on the outside flows into the pressure reduction device 203. The pressure of the high pressure liquid refrigerant that flowed into the pressure reducing device 203 is reduced by the pressure reducing device 203 to a low temperature low pressure gas-liquid two-phase refrigerant and then flows out of the pressure reducing device 203. The low-temperature, low-pressure gas-liquid two-phase refrigerant that flowed out of the pressure reduction device 203 flows into the heat exchanger 204 on the inside. The low-temperature, low-pressure two-phase gas-liquid refrigerant that flowed into the heat exchanger 204 on the inside receives heat from the air in the room and evaporates, and then flows out of the heat exchanger 204 on the inside as a low-pressure gas refrigerant or two-phase gas-liquid refrigerant. liquid. At this time, the air in the room is cooled. The low-pressure gas refrigerant or gas-liquid two-phase refrigerant that flowed out from the heat exchanger 204 on the inside is sucked into the damper 3 of the compressor chamber 1. The low-pressure gaseous refrigerant occupied by the refrigerant sucked into the damper 3 of the compressor chamber 1 is compressed by compression mechanism 20 in compressor 1 to high-temperature, high-pressure refrigerant in gaseous state. The high-temperature, high-pressure refrigerant in the gaseous state is again pushed out of the compressor 1. This means that if the 200 refrigerant cycle device operates in the cooling mode, the refrigerant circulates in the manner shown by the dotted arrows in Fig. 2.

(Oil Supply Component 100)

In the compressor 1 according to the proposed embodiment 1, the oil supply component 100 is connected to the end part 41 of the rotary shaft 40 in order to improve the ability to supply the oil 6 of the refrigerating machine to the sliding parts of the compression mechanism 20 in the state in which the rotary shaft 40 falls into the range of low revolutions. The oil supply component 100 of the present embodiment 1 is described in detail below.

- 9 CZ 2024 - 210 A3

Fig. 3 is a vertical sectional view showing the oil supply component of embodiment 1 connected to the end portion of the compressor rotary shaft. Giant. 4 is a vertical sectional view showing the oil supply component according to embodiment 1. FIG. 5 is a top view showing the oil supply component according to embodiment 1.

The oil supply component 100 is made, for example, of a plate-like part of metal. In the proposed embodiment 1, a plate-like part made of GB-65Mn spring steel is used to manufacture the oil supply component 100. It should be noted that the material of the oil supply component 100 is not specifically defined and other sheet metal parts such as SPCC, SUS304 or S50C may be used to manufacture the oil supply component 100.

As shown in Figs. 3 to 5 , the oil supply component 100 includes a main plate part 110 and a plurality of plug-in parts 120. The main plate part 110 is formed as a flat plate, for example. For example, a through hole 111 is formed on the main plate part in an essentially central position. Each of the plug-in parts 120 protrudes from the main plate part 110 in a position near the outer peripheral part 112 of the main plate part 110 in relation to the through hole 111. Each of the plug-in parts 120 is inserted into the oil supply hole 42 in the rotary shaft 40. More specifically, the plurality of plug-in parts 120 are inserted into the oil supply hole 42 in the rotary shaft 40, and the outer surfaces of the plurality of plug-in parts 120 are in contact with the inner peripheral surface 46 of the rotary shaft 40 so that the oil supply component 100 is attached to the end part 41 of the rotary shaft 40.

In the oil supply component 100 of the above-described configuration, a through hole 111 is formed on the inner peripheral side in relation to a plurality of plug-in parts 120 to be inserted into the oil supply hole 42. Based on this, the through hole 111 has a smaller diameter than the diameter of the oil supply hole 42 in the rotary shaft 40. As already described above, the oil supply component 100 has such a configuration that allows the oil 6 of the cooling machine to be sucked into the supply hole 42 of oil in the rotary shaft 40 from the through hole 111 with a diameter smaller than the diameter of the oil supply hole 42 in the rotary shaft 40. The oil supply component 100 can thus improve the ability to supply the oil 6 of the cooling machine to the sliding elements of the compression mechanism 20 in the state, in which rotating shaft 40 falls into the range of low revolutions. This means that the reliability of the compressor 1 can be ensured even in the state in which the rotating shaft 40 falls into the range of low revolutions.

There is a conventional oil supply component including a main plate part which is formed in the same manner as the main plate part 110 of the oil supply component 100 according to the present embodiment 1. This conventional oil supply component has a problem in that it is connected tight to the rotary shaft of the compressor. Accordingly, each of the plug-in parts 120 in the oil supply component 100 according to the present embodiment 1 has the following configuration.

Each of the plug-in parts 120 specifically includes a base end part 121 and a top end part 125. The base end part 121 is connected to the main plate part 110 at the end part 122, which is one end part of the base end part 121. 122 is identical to the second end part. The end portion 126, which is one end portion of the apex end portion 125, is connected to the end portion 123, which is another end portion of the base end portion 121. The end portion 127, which is another end portion of the apex end portion 125, is the apex end of the sliding portion. 120. It should be noted that end part 123 is equivalent to the third end part, end part 126 is equivalent to the fourth end part and end part 127 is equivalent to the fifth end part. The place where the end part 123 of the base end part 121 and the end part 126 of the top end part 125 are connected is hereinafter referred to as "connecting part 130".

[0048] The plug-in parts 120, each of which has the configuration described above, have the position described below. It should be noted that in the description of the position of the plug-in parts 120 there is an imaginary straight line passing

- 10 CZ 2024 - 210 A3 through the opening 111 on the main plate part 110 and perpendicular to the main plate part 110, defined as the first imaginary straight line L1. The first imaginary line L1 is substantially parallel to the center of rotation of the rotary shaft 40 when the oil supply component 100 is connected to the end portion 41 of the rotary shaft 40. In other words, the first imaginary line L1 is substantially parallel to the direction in which the opening 42 extends for the oil supply, when the oil supply component 100 is connected to the end part 41 of the rotary shaft 40. Based on the above-described definition of the first imaginary line L1, in each of the basic end parts 121, the end part 123 is located in the farthest position from the first imaginary line L1 . In each of the top end parts 125, the end part 126 is located in the farthest position from the first imaginary line L1. This means that in each of the plug-in parts 120, the connecting part 130 is located in the farthest position from the first imaginary line L1.

[0049] In the oil supply component 100 in which each of the plug-in parts 120 has the above-mentioned position, it is sufficient that each connecting part 130 and each end part 127 are placed in the manner described below depending on the diameter of the oil supply hole 42 in the rotary shaft 40 to which the oil supply component 100 is connected. This makes it easier to connect the oil supply component 100 to the rotary shaft 40 compared to a conventional oil supply component.

More precisely, the imaginary circle that touches the outer surface of the connecting part 130 of each of the plug-in parts 120 is defined as the first imaginary circle C1. The diameter of the first imaginary circle C1 is defined as the first diameter D1. The imaginary circle that touches the outer surface of the end part 127 of the top end part 125 of each of the plug-in parts 120 is further defined as the second imaginary circle C2. The diameter of the second imaginary circle C2 is defined as the second diameter D2. The diameter of the oil inlet hole 42 formed in the rotary shaft 40 is defined as the third diameter D3. From the above-described diameter definitions, it follows that the first diameter D1 is greater than the third diameter D3, while the second diameter D2 is smaller than the third diameter D3.

The reasons why the oil supply component 100 according to the present embodiment 1 can be connected to the rotary shaft 40 more easily than with a conventional oil supply component are explained below with reference to a schematic representation of the oil supply component 100 according to the present embodiment 1 and a schematic depiction of oil supply components according to comparative design examples.

Fig. 6 is a schematic side view showing the oil supply component according to embodiment 1. Giant. 7 and 8 are schematic illustrations of the oil supply component according to the comparative example, viewed from the side. It should be noted that Fig. 6 to 8 show an example of a pair of opposite plug-in parts.

In each of the above-described plug-in parts 120 of the oil supply component 100 according to the proposed embodiment 1 shown in Fig. 6, in each of the basic end parts 121, the end part 123 is located in the farthest position from the first imaginary line L1. In each of the top end parts 125, the end part 126 is located in the farthest position from the first imaginary line L1.

In each of the plug-in parts 320 of the oil supply component 300 according to the comparative example embodiment shown in Fig. 7, the entire basic end part 321 is equidistant from the first imaginary line L1. The vertex end part 325 is also the same distance from the first imaginary line L1. This means that in the oil supply component 300 according to the comparative embodiment shown in Fig. 7, the plug-in parts 320 extend from the main plate part 310 parallel to the first imaginary straight line L1. The retractable parts 320 extend parallel to each other. The catch elements of the oil supply component described in the Japanese Laid-Open Patent Publication No. S63-154787 listed in the citation list have the same shape as the sliding parts 320 shown in Fig. 7 .

- 11 CZ 2024 - 210 A3

In each of the plug-in parts 420 of the oil supply component 400 according to the comparative example shown in Fig. 8, the entire basic end part 421 is equidistant from the first imaginary line L1. In the apex end portion 421, the distance from the first imaginary line L1 decreases as the apex end portion 421 extends from the base end portion 421 toward the apex end. This means that in the oil supply component 400 according to the comparative example of the embodiment shown in Fig. 8, the basic end part 421 of the plug-in part 420 extends from the main plate part 410 parallel to the first imaginary straight line L1. The basic end parts 421 of the plug-in parts 420 extend parallel to each other.

[0056] When the oil supply component is connected to the rotary shaft, each of the plug parts of the oil supply component is first inserted into the oil supply hole in the rotary spindle so that the outer surface of each of the plug parts is in contact with the inner peripheral surface of the rotator. shaft. Each of the plug-in parts is inserted into the oil supply hole until the oil supply component reaches the specified connection position. Each of the plug-in parts whose outer surface is in contact with the inner peripheral surface of the rotary shaft is pressed by the inner peripheral surface of the rotary shaft and is deformed. This causes an elastic force to be generated in each of the plug-in parts, the outer surface of which is in contact with the inner peripheral surface of the rotating spindle. The elastic force in the plug-in part is the reaction force generated in the deformed plug-in part when the deformed plug-in part returns to its original shape. The oil supply component is attached to the rotary shaft by the elastic force generated in each of the plug-in parts inserted into the oil supply hole in the rotary shaft. The oil supply component is connected to the rotary shaft in the manner described above.

In the oil supply component 300 according to the comparative embodiment shown in Fig. 7, each of the plug-in parts 320 extends parallel to the first imaginary straight line L1. Based on this construction, in the case where the oil supply component 300 according to the comparative embodiment shown in Fig. 7 is attached to the rotary shaft 40 in the manner described above, the diameter of the imaginary circle that contacts the outer surface of the apex end of each of the plug-in parts must be 320, greater than the third diameter D3, which is the diameter of the opening 42 for oil supply. Therefore, in the oil supply component 300 according to the comparative example embodiment shown in Fig. 7, it is difficult to insert the top end of each of the plug-in parts 320 into the oil supply hole 42. In the oil supply component 300 according to the comparative example shown in Fig. 7, each of the plug parts 320 is inserted into the oil supply hole 42, while the main part of the outer surface of each of the plug parts 320 is in contact with the inner peripheral surface 46 of the rotary spindle 40 and until the oil supply component 300 reaches the specified connection position. For this reason, the oil supply component 300 according to the comparative embodiment shown in Fig. 7 exhibits an increase in resistance caused by the insertion of each of the plug-in parts 320 into the oil supply hole 42. Therefore, it is difficult to connect the component 300 for the supply of oil according to the comparative example of the embodiment shown in Fig. 7 to the rotating spindle 40.

In the oil supply component 400 according to the comparative embodiment shown in Fig. 8 , for each of the top end portions 421, the distance from the first imaginary straight line L1 decreases as the top end portion 421 extends from the base end portion 421 toward the top end. . Based on this construction, the diameter of the imaginary circle that touches the outer surface of the apex end of each of the apex end parts 421 may be smaller than the third diameter D3, which is the diameter of the hole 42, in the oil supply component 400 according to the comparative example embodiment shown in Fig. 8 for oil supply. The reason is that even when the apex end of each of the apex end portions 421 is placed in the position described above, the outer surface of each of the base end portions 421 when the plug portions 420 are inserted into the oil supply hole 42 may still be in contact with the inner by the peripheral surface 46 of the pivot pin 40. In this design, it is easier for the oil supply component 400 according to the comparative example embodiment shown in Fig. 8 to insert the top end of each of the plug-in parts 420 into the oil supply hole 42 than it is for the oil supply component 300 oil according to the comparative example shown in Fig. 7.

- 12 CZ 2024 - 210 A3

However, in the oil supply component 400 according to the comparative embodiment shown in Fig. 8 , each of the basic end parts 421 of the plug-in parts 420 extends parallel to the first imaginary straight line L1. Accordingly, in the oil supply component 400 according to the comparative example embodiment shown in Fig. 8, each of the plug portions 420 is inserted into the oil supply hole 42, while the main portion of the outer surface of each of the base end portions 421 is in contact with the inner peripheral surface 46 of the rotary shaft 40 and until the moment when the oil supply component 400 reaches the specified connection position. For this reason, the oil supply component 400 according to the comparative example embodiment shown in Fig. 8 exhibits an increase in resistance caused by the insertion of each of the insertion parts 420 into the oil supply hole 42. Therefore, it is also difficult to connect the oil supply component 400 according to the comparative example embodiment shown in Fig. 8 to the rotary shaft 40 similarly to the oil supply component 300 according to the comparative example embodiment shown in Fig. 7.

[0060] In contrast, in the oil supply component 100 according to the present embodiment, the second diameter D2 of the second imaginary circle C2, which touches the outer surface of each of the end parts 127, which are the top ends of the plug-in parts 120, may be made smaller than the third diameter D3, which is the diameter of the above-described opening 42 for oil supply. In this construction, the oil supply component 100 of the present embodiment 1 is easy to insert into the oil supply hole 42 by each of the end portions 127, which are the top ends of the plug portions 120. In this case, in the oil supply component 100 according to the present embodiment 1, the first diameter D1 of the first imaginary circle C1 that touches the outermost surface of each of the connecting parts 130 of the plug-in parts 120 can be made larger than the third diameter D3, which is the diameter described above hole 42 for oil supply. In this construction, even if the second diameter D2 is made smaller than the third diameter D3, it is still possible to connect the oil supply component 100 according to the proposed embodiment 1 to the rotary shaft 40.

In the oil supply component 100 according to the present embodiment 1, each of the plug parts 120 is inserted into the oil supply hole 42, while only the outer surface of the connecting part 130 of each plug part is in contact with the inner peripheral surface 46 of the rotary shaft 40 120 and until the moment when the oil supply component 100 reaches the specified connection position. This means that the connecting part 130 of each of the plug parts 120 is in contact with the inner peripheral surface 46 of the rotary shaft 40, whereby the oil supply component 100 is attached to the rotary shaft 40. Based on this configuration, the oil supply component 100 according to the present embodiment can 1 to reduce the resistance caused by inserting each of the plug-in parts 120 into the hole 42 for the oil supply. Therefore, the connection of the oil supply component 100 according to the present embodiment 1 to the rotating shaft 40 is easier than with a conventional oil supply component.

[0062] It should be noted that in the proposed embodiment 1 shown in Fig. 4, each of the plug-in parts 120 is formed in the above-described shape by forming inclined surfaces on the base end part 121 and on the top end part 125. Each of the base end parts 121 More specifically contains the first cured Câst 124 surface connected to the end Câsti 126 top end -end Câsti 125 and pnblizing to the first imaginary Primce L1, as the end of the end of the end of the end of the end of the terminals 123. a second inclined surface portion 128 connected to the end portion 123 of the base end portion 121 and approaching the first imaginary straight line L1 as the apex end portion 125 extends from the end portion 126 toward the end portion 127. It should be noted that the base end portion 121 may contain the first inclined portion 124 of the surface in its entirety, or may partially contain the first inclined portion 124 of the surface. The top end portion 125 may include the second inclined surface portion 128 in its entirety, or may partially include the second inclined surface portion 128. The sliding part 120 is formed in the above-described manner by the first inclined part 124 of the surface and the second inclined

- 13 CZ 2024 - 210 A3 part 128 of the surface, so that the plug-in part 120 is created in an easy way, which facilitates the production of the component 100 for the oil supply.

In the case when the plug-in part 120 is formed by the first inclined part 124 of the surface and the second inclined part 128 of the surface, it is convenient to determine the angles of the first inclined part 124 of the surface and the second inclined part 128 of the surface in the manner described below. With reference to the schematic representation of the oil supply component 100 shown in Fig. 6, the optimal angles of the first inclined surface portion 124 and the second inclined surface portion 128 are described below.

As shown in Fig. 6 , the imaginary line that touches the outer surface of the connecting part 130 and extends parallel to the first imaginary line L1 is defined as the second imaginary line L2. On the basis of the definition described above, it is preferable that the angle β formed between the second imaginary line L2 and the second inclined part 128 of the surface of the top end part 125 is greater than the angle α formed between the second imaginary line L2 and the first inclined part 124 of the surface of the base end part 121. Due to it is sufficient for the first inclined part 124 of the surface to make such an angle with respect to the second imaginary straight line L2, that the basic end part 121 is not in contact with the inner peripheral surface 46 of the pivot pin 40 when the plug-in parts 120 are inserted into the hole 42 for the oil supply in the rotating shaft 40. On the other hand, it is preferable that the end portion 127, which is the apex end of the apex end portion 125, is placed in such a position that the second diameter D2 is reduced to a minimum to facilitate insertion into the oil supply hole 42 in the rotating shaft 40. Based on this, it is preferable that the angle β formed between the second imaginary line L2 and the second inclined part 128 of the surface of the top end part 125 is greater than the angle α formed between the second imaginary line L2 and the first inclined part 124 of the surface of the base end part 121.

[0065] It is preferable, as shown in Fig. 3 to 6, that the oil supply component 100 includes at least one contact part 140, which is arranged on the outer peripheral part 112 of the main plate part 110 and in contact with the end part 41 of the rotary pin 40. It should be noted that in the proposed embodiment 1, a total of four contact parts 140 are arranged, each of which is placed between the plug-in parts 120. Once each of the plug-in parts 120 is inserted into the oil supply hole 42 in the rotary shaft 40, the component 100 for the oil supply stops at a position where the contact parts 140 come into contact with the end part 41 of the rotary spindle 40. Accordingly, the component 100 for the oil supply includes the contact parts 140 for facilitating the positioning of the component 100 for the oil supply at the time of connecting the component 100 for oil supply to the rotary handle 40. In addition, the oil supply component 100 includes contact parts 140, so that the oil supply component 100 can be prevented from further entering the oil supply hole 42 when driving the compressor 1. Thus, the oil supply component 100 includes a contact part 140, which improves the reliability of compressor 1.

[0066] It should be noted that the number of plug-in parts 120 occupied in the component 100 for the supply of oil is not specifically defined, assuming that a plurality of plug-in parts 120 are occupied here. This means that the number of plug-in parts 120 occupied in the oil supply component 100 is two or more. However, it is preferable that the number of plug-in parts 120 is four. It is also preferable that two of the four plug-in parts 120 are placed opposite each other, whereby the two remaining plug-in parts 120 are also placed opposite each other. Component 100 for oil is more specific to the turning point of 40 with the use of the extent of this configuration, it is necessary to decline with the honor of the 120 ÿ ÿ câsti 120 for a larger strong. In other words, more force is needed to insert the plug-in parts 120 into the oil inlet hole 42. On the other hand, if the number of the plug-in parts 120 is increased excessively, the elastic force of each of the plug-in parts 120 is reduced, and consequently the oil supply component 100 to the rotary shaft 40 is attached with reduced stability. It is convenient to apply the elastic force of the plug-in parts 120 to the inner peripheral surface 46 of the rotary spindle 40 axially symmetrically with the axis extending in the direction in which the oil supply hole 42 is formed, so that the oil supply component 100 is fixed to the rotary shaft 40 in a stable manner . This means that it is preferable that the two plug-in parts 120 are placed

- 14 CZ 2024 - 210 A3 mutually opposite. Based on this, it is preferable that the oil supply component 100 contains four plug-in parts 120. It is also preferable that two of the four plug-in parts 120 are positioned opposite each other, whereby the two remaining plug-in parts 120 are also positioned opposite each other.

[0067] The oil supply component 100 according to the above-described proposed embodiment 1 is arranged in a compressor 1 containing a rotary shaft 40, in which an oil supply opening 42 is formed, which is opened at the end part 41 for the purpose of supplying the oil 6 of the refrigerating machine sucked into of the opening 42 for supplying oil to the compression mechanism 20. The component 100 for supplying oil includes a main plate part 110 and a plurality of plug-in parts 120. A through hole 111 is formed on the main plate part 110. Each of the plug-in parts 120 protrudes from the main plate part 110 in a position , which is located near the outer peripheral part 112 of the main plate part 110 in relation to the passage of the hole 111. Each of the plug-in parts 120 is inserted into the oil supply hole 42. Each of the plug-in parts 120 includes a base end part 121 and a top end part 125. The base end part 121 is connected to the main plate part 110 at the end part 122. The top end part 125 is connected to the end part 123 of the base end part 1 21 at the end of section 126 The end part 127 of the top end part 125 is the top end of the plug part 120. In the case where the imaginary line passes through the through hole 111 and is perpendicular to the main plate part 110, it is defined as the first imaginary line L1, in each of the basic end parts 121, end Part 123 is located in the position farthest from the first imaginary line L1. In each of the top end parts 125, the end part 126 is located in the farthest position from the first imaginary line L1. In each of the plug-in parts 120 of the oil supply component 100, the coupling part 130 is in contact with the inner peripheral surface 46 of the rotary shaft 40, and therefore the oil supply component 100 is fixed to the rotary shaft 40, whereby the coupling part 130 is the place where they are connected end part 123 of base end part 121 and end part 126 of top end part 125.

[0068] In the oil supply component 100 with the configuration described above, it is easy to insert each of the end parts 127, which are the top ends of the plug parts 120, into the oil supply hole 42. The oil feed component 100 of the configuration described above can also reduce the resistance caused by inserting each of the plug portions 120 into the oil feed hole 42 . Connecting the oil supply component 100 with the configuration described above to the rotary shaft 40 is therefore easier than with conventional oil supply components.

Done 2

The component 100 for the oil supply has the configuration described below, in which it is possible to reduce the number of components of the compressor 1 compared to the embodiment 1, and thus it is possible to reduce the number of standard hours for the assembly of the compressor 1. It should be noted that the elements that are not in the proposed embodiment 2 specifically described, are the same as the elements in embodiment 1 and the same functions and configurations as those found in embodiment 1 are denoted by the same reference numerals and described below.

Fig. 9 is a vertical sectional view showing the oil supply component according to embodiment 2. FIG. 10 is a bottom view showing the oil supply component according to embodiment 2.

In the oil supply component 100 according to the present embodiment 2, one of the plug parts 120 is provided with a blade part 145 formed by twisting the plate part and is connected to the end part 127 of the top end part 125.

More specifically, the third imaginary line L3 shown in Figs. 9 and 10 marks the position of the center of the oil supply hole 42 when the oil supply component 100 is connected to the rotary shaft 40. The shape of the vane part 145, which is a plate part, is shown in a view from its one end part near the end part 127 of the plug-in part 120 towards the other end part opposite to the one end part. In this case, the blade part 145 extends from the end part 127 of one of the plug-in parts 120 towards the third imaginary line L3. The blade portion 145 is also bent in position on the third imaginary line L3 and accordingly extends along the third imaginary line L3.

- 15 CZ 2024 - 210 A3

The blade portion 145, which is a plate-like portion, is twisted at the point from which the blade portion 145 extends along the third imaginary line L3. Once the oil supply component 100 is connected to the rotary shaft 40, the twist point of the vane portion 145 is positioned inside the oil supply port 42 to act as a centrifugal pump.

This means that the oil supply component 100 according to the present embodiment 2 has such a configuration that the centrifugal pump forms an integral part of the oil supply component 100. Based on this, the compressor 1 equipped with the oil supply component 100 according to the present embodiment 2 does not need the centrifugal pump 45 shown in the embodiment 1. Therefore, by using the oil supply component 100 according to the present embodiment 2, the number of components of the compressor 1 can be reduced. Simultaneously with the connection of the supply component 100 oil according to the proposed embodiment 2 to the rotating shaft 40, a centrifugal pump is also installed in the rotating shaft 40. By using the component 100 for the oil supply according to the proposed embodiment 2, the number of standard hours to assemble the compressor 1 can be reduced.

Claims (8)

1. An oil supply component arranged in a compressor containing a rotary shaft, in which an oil supply hole is formed for supplying the oil of the refrigerating machine sucked into the oil supply hole of the compression mechanism, whereby this oil supply hole is opened at the first end part and this the first end part is one end part of the rotary shaft, where this oil supply component includes: the main plate part, on which a through hole is formed; and a plurality of plug-in parts, each of which protrudes from the main plate part in a position near the outer peripheral part of the main plate part in relation to the through hole, whereby this plurality of plug-in parts is inserted into the oil supply hole, where each of these plug-in parts includes a base end a part connected to the main board part at the second end part, whereby this second end part is one end part of the base end part, and a top end part connected to a third end part at the fourth end part, whereby this third end part is another end part of the base end part , the fourth end part is one end part of the top end part, the top end part has a fifth end part, whereby this fifth end part is another end part of the top end part, and the fifth end part is the top end of the insert part, where the imaginary straight line passing through the through hole, which is perpendicular to the main plate part is defined as the first imaginary line, in each of the base end parts the third end part is located in the farthest position from the first imaginary line, and in each of the top end parts the fourth end part is located in the farthest position from the first imaginary lines, and in each of the insertion parts, the coupling part is in contact with the inner peripheral surface of the rotary shaft, and thereby the oil supply component is fixed to the rotary shaft, through which the coupling part is the place where the third end part of the base end part and fourth terminal part of the apex terminal part. 2. The oil supply component according to claim 1, wherein the imaginary circle that touches the outer surface of the connecting part of each of the plug-in parts is defined as the first imaginary circle, the diameter of the first imaginary circle is defined as the first diameter, the imaginary circle that touches the outer surface of the fifth end part of the top end part of each of the plug-in parts is defined as a second imaginary circle, the diameter of the second imaginary circle is defined as the second diameter, and the diameter of the oil supply hole formed in the rotary shaft is defined as the third diameter, - 17 CZ 2024 - 210 A3 whereby the first diameter is greater than the third diameter, the second diameter is smaller than the third diameter. 3. An oil supply component according to claim 1 or 2 comprising a contact part arranged on the outer peripheral part of the main plate part, which is in contact with the first end part of the rotary shaft. 4. An oil supply component according to any one of claims 1 to 3, wherein each of the base end portions includes a first inclined surface portion connected to the fourth end portion of the apex end portion and approaching a first imaginary straight line as the base end portion extends from the third end portion portions in the direction of each of the apex end portions includes a second inclined surface portion connected to the third end portion of the base end portion and approximating the first imaginary straight line as the apex end portion extends from the fourth end portion toward the fifth end portion, and where the imaginary line which touching the outer surface of the connecting part and parallel to the first imaginary line, is defined as the second imaginary line, the angle formed between the second imaginary line and the second inclined part of the surface is greater than the angle formed between the second imaginary line and the first inclined part of the surface. 5. An oil supply component according to any one of claims 1 to 4, which includes four plug-in parts, where two of the plug-in parts are located opposite each other, and the remaining two plug-in parts are located opposite each other. 6. An oil supply component according to any one of claims 1 to 5, wherein one of the plug-in parts is provided with a blade part formed by twisting the plate-like part and connected to the fifth end part. 7. Compressor containing: rotary electric machine; rotating shafts connected to a rotating electric machine for the purpose of turning it to help the power of the rotating electric machine; a compression mechanism connected to the rotary shaft, which is configured to compress the refrigerant drawn in from the outside by means of the power of a rotary electric machine transmitted through the rotary shaft; the outer layer of the compressor, for capturing the oil of the cooling machine inside, whereby the rotating electric machine, rotating shafts and compression mechanism are stored inside this outer layer of the compressor; and an oil supply component according to any one of claims 1 to 6, whereby an oil supply hole is formed and opened in the rotary shaft at one end part of the rotary shaft for the purpose of supplying the oil of the refrigerating machine sucked into the oil supply hole to the compression mechanism, and - 18 CZ 2024 - 210 A3 each of the plug-in parts of the oil supply component is inserted into the oil supply hole, the connecting part of each of the plug-in parts is in contact with the inner peripheral surface of the rotary shaft, whereby the oil supply component is attached to the rotary shaft. 8. Refrigerant cycle equipment containing: a compressor according to claim 7; cooler for transferring the heat of the refrigerant compressed by the compressor; a pressure reduction device configured to reduce the pressure of coolant flowing from the cooler; and an evaporator for evaporating the coolant flowing from the pressure reduction device.