WO2023012852A1

WO2023012852A1 - Hermetic compressor and refrigeration cycle device

Info

Publication number: WO2023012852A1
Application number: PCT/JP2021/028556
Authority: WO
Inventors: 拓真塚本; 友宏井柳; 宏樹長澤
Original assignee: 三菱電機株式会社
Priority date: 2021-08-02
Filing date: 2021-08-02
Publication date: 2023-02-09
Also published as: CN117716130A; JPWO2023012852A1

Abstract

This hermetic compressor is provided with a hermetic container constituting an outer hull and a compression mechanism part accommodated in the hermetic container. The compression mechanism part is provided with a hollow cylindrical cylinder having a vane groove provided in a radial direction, a rolling piston eccentrically rotating along an inner peripheral surface of the cylinder, a partitioning vane reciprocating inside the vane groove and partitioning a space between the inner peripheral surface of the cylinder and the rolling piston into a high-pressure side and a low-pressure side, and a vane spring urging the vane to be brought into contact with the rolling piston. A load center position due to the vane spring gets closer to the low-pressure side than a center position of the vane.

Description

Hermetic compressor and refrigeration cycle equipment

The present disclosure relates to a hermetic compressor and a refrigeration cycle device.

A rotary compressor is generally composed of a sealed container, a compression mechanism section disposed inside the container, and an electric motor (see Patent Document 1, for example). The compression mechanism includes a hollow cylindrical cylinder, a shaft rotatable around a central axis, a rolling piston that performs eccentric rotational motion inside the cylinder as the shaft rotates, and a cylinder that eccentrically rotates as the rolling piston rotates. and a spring mechanism such as a coil spring provided on the back surface of the vane for pressing the tip of the vane against the rolling piston.

WO2004/053335

In the rotary compressor described in Patent Document 1, a rolling piston performs an eccentric rotational movement in a cylinder housed in a closed container, and vanes pressed against the rolling piston by the biasing force of a spring mechanism partition the space inside the cylinder. This compresses the refrigerant. At this time, since the high-pressure space and the low-pressure space are separated by the vane as a boundary, a load is applied in the direction from the high-pressure space side to the low-pressure space side on the tip side of the vane that contacts the rolling piston. This load causes a moment in the vane, causing the vane to tilt. Then, the reciprocating motion of the vane in an inclined state increases the frictional force between the vane and the vane groove of the cylinder. There was a problem of reduced reliability or abnormal noise due to collision of parts.

The present disclosure has been made in order to solve the above problems, and suppresses the generation of abnormal noise when the vanes reciprocate inside the vane grooves, and has a highly reliable hermetic compressor and refrigeration cycle. The purpose is to provide a device.

A hermetic compressor according to the present disclosure includes a hermetic container that forms an outer shell, and a compression mechanism that is housed in the hermetic container. A cylindrical cylinder, a rolling piston that rotates eccentrically along the inner peripheral surface of the cylinder, and a rolling piston that reciprocates inside the vane groove to pressurize the space between the inner peripheral surface of the cylinder and the rolling piston under high pressure. and a vane spring that urges the vane to contact the rolling piston, and the center position of the load by the vane spring is closer to the low pressure side than the center position of the vane. ing.

A refrigeration cycle apparatus according to the present disclosure includes the hermetic compressor, the outdoor heat exchanger, the expansion device, and the indoor heat exchanger.

According to the hermetic compressor and refrigeration cycle device according to the present disclosure, the center position of the load by the vane spring is closer to the low pressure side than the center position of the vane. Therefore, rather than making the load center position of the vane spring the center position of the vane, which is the normal load center position, the moment generated by the load applied to the tip side of the vane should be alleviated. can be done. As a result, the inclination of the vane is suppressed, so that the generation of abnormal noise when the vane reciprocates inside the vane groove can be suppressed, and collision of parts is suppressed, so that high reliability can be obtained. can be done.

1 is a cross-sectional view of a hermetic compressor according to Embodiment 1. FIG. 2 is a cross-sectional view of a compression mechanism portion of the hermetic compressor according to Embodiment 1. FIG. FIG. 4 is a cross-sectional view of a groove fixing structure of a vane spring to a cylinder-side spring mounting hole of the hermetic compressor according to Embodiment 1, viewed from above. FIG. 4 is a plan view of a structure for press-fitting and fixing a vane spring into a cylinder-side spring mounting hole of the hermetic compressor according to Embodiment 1; 1 is a schematic configuration diagram of a refrigeration cycle apparatus including a hermetic compressor according to Embodiment 1; FIG. 2 is a schematic cross-sectional view of the electric motor of the hermetic compressor according to Embodiment 1. FIG. 4 is a cross-sectional force diagram around vanes of the hermetic compressor according to Embodiment 1. FIG. FIG. 4 is a cross-sectional view showing a vane pressing structure of the hermetic compressor according to Embodiment 1; FIG. 7 is a cross-sectional view showing a first modification of the pressing structure of the vanes of the hermetic compressor according to Embodiment 1; 8 is a cross-sectional view showing a second modification of the pressing structure of the vanes of the hermetic compressor according to Embodiment 1. FIG. FIG. 10 is a cross-sectional force diagram around the vane of the hermetic compressor according to Embodiment 2; FIG. 7 is a diagram showing the shape of vanes of a hermetic compressor according to Embodiment 2; FIG. 8 is a cross-sectional view showing a vane pressing structure of a hermetic compressor according to Embodiment 2; FIG. 8 is a cross-sectional view showing a first modification of the pressing structure of the vanes of the hermetic compressor according to Embodiment 2;

A hermetic compressor 100 and a refrigeration cycle device 200 according to an embodiment will be described below with reference to the drawings. It should be noted that the present disclosure is not limited by the embodiments described below. Also, in the following drawings, the size relationship of each component may differ from the actual size. Also, in the following description, terms representing directions (for example, "up", "down", "right", "left", "front", "back", etc.) are used as appropriate for ease of understanding. For the purpose of description, these terms are not intended to limit this disclosure. Unless otherwise specified, these directional terms mean directions when the hermetic compressor 100 is viewed from the front side (front side). Also, in each figure, the same reference numerals denote the same or corresponding parts, which are common throughout the specification.

Embodiment 1.
FIG. 1 is a cross-sectional view of a hermetic compressor 100 according to Embodiment 1. FIG. FIG. 2 is a cross-sectional view of the compression mechanism portion 20 of the hermetic compressor 100 according to Embodiment 1. FIG. 2 is a cross-sectional view of the compression mechanism 20 taken along line AA of FIG. 1 and viewed from above.

The hermetic compressor 100 according to Embodiment 1 is, for example, a one-cylinder rotary compressor, and has a function of sucking a fluid such as a refrigerant, compressing it, and discharging it in a high-temperature, high-pressure state. As shown in FIG. 1, this hermetic compressor 100 includes a hermetic container 10 forming an outer shell. This sealed container 10 is composed of an upper container 11 and a lower container 12 .

A discharge pipe 102 is fixed through the upper surface of the upper container 11 of the closed container 10 . The discharge pipe 102 discharges high-pressure refrigerant gas to the outside of the sealed container 10 . The fixed portion between the discharge pipe 102 and the upper container 11 is joined by welding or the like, for example.

A compression mechanism 20, an electric motor 30, a crankshaft 40, and other components are housed inside the sealed container 10. The compression mechanism section 20 is housed below the sealed container 10 , and the electric motor 30 is housed above the sealed container 10 . The compression mechanism portion 20 and the electric motor 30 are connected by a crankshaft 40 . The crankshaft 40 transmits the rotational motion of the electric motor 30 to the compression mechanism section 20 , and the compression mechanism section 20 compresses the refrigerant gas by the transmitted rotational force. discharged inside. The closed container 10 is filled with compressed high-temperature, high-pressure refrigerant gas, and refrigerating machine oil is stored below the closed container 10 , i.e., at the bottom thereof, to lubricate the compression mechanism 20 . An oil pump (not shown) is provided below the crankshaft 40. As the crankshaft 40 rotates, the oil pump pumps up the refrigerating machine oil stored in the bottom of the sealed container 10, Lubricate moving parts. Thereby, the mechanical lubricating action of the compression mechanism portion 20 is ensured.

The crankshaft 40 is composed of a main shaft portion 41, an eccentric shaft portion 42, and a sub shaft portion 43, which are formed in order of the main shaft portion 41, the eccentric shaft portion 42, and the sub shaft portion 43 in the axial direction. The electric motor 30 is shrink-fitted or press-fitted to the main shaft portion 41 and fixed, and the cylindrical rolling piston 22 is slidably fitted to the eccentric shaft portion 42 .

The compression mechanism section 20 compresses the low-pressure refrigerant gas sucked into the sealed container 10 into a high-pressure refrigerant gas by the rotational driving force supplied from the electric motor 30, and compresses the compressed high-pressure refrigerant gas into the compression mechanism section 20. is ejected upward.

The compression mechanism section 20 includes a rolling piston 22, a cylinder 23, an upper bearing 24, a lower bearing 25, and vanes 26, as shown in FIGS. The cylinder 23 is internally provided with a cylindrical space, ie, a cylinder chamber 23a, which is open at both ends in the axial direction. In the cylinder chamber 23a, there are provided an eccentric shaft portion 42 of a crankshaft 40 that performs eccentric motion in the cylinder chamber 23a, a rolling piston 22 fitted to the eccentric shaft portion 42, an inner periphery of the cylinder chamber 23a and the rolling piston. A vane 26 that partitions the space formed by the outer periphery of 22 is housed.

The cylinder 23 has a back pressure chamber 23b which communicates with the space outside the cylinder 23 within the sealed container 10, and a vane groove 23c which extends in the radial direction of the cylinder 23 and communicates the cylinder chamber 23a and the back pressure chamber 23b. have. A substantially rectangular parallelepiped vane 26 is accommodated in the vane groove 23c. The vanes 26 reciprocate in the radial direction while sliding inside the vane grooves 23c.

FIG. 3 is a cross-sectional view of the groove fixing structure of the vane spring 28 in the cylinder-side spring mounting hole 29 of the hermetic compressor 100 according to the first embodiment. FIG. 4 is a plan view of a structure for press-fitting and fixing the vane spring 28 into the cylinder-side spring mounting hole 29 of the hermetic compressor 100 according to the first embodiment. 3 and 4 are plan views of cross sections taken along arrow C in FIG.

As shown in FIG. 3, the back pressure chamber 23b of the cylinder 23 has a vane spring 28 that biases the vane 26 to abut against the rolling piston 22, and a cylinder-side spring mounting hole 29 that accommodates the vane spring 28. is provided. An end portion 28a of the vane spring 28 opposite to the vane 26 is fixed by a groove fixing structure. In the groove fixing structure, the end portion 28a of the vane spring 28 is attached to the enlarged inner diameter portion 29a formed by enlarging the inner diameter of the cylinder-side spring mounting hole 29 according to the enlarged outer diameter of the end portion 28a of the vane spring 28. It is a structure that is fixed by storing.

The structure for fixing the end portion 28a of the vane spring 28 opposite to the vane 26 to the cylinder 23 may be a press-fit fixing structure instead of the groove fixing structure. That is, as shown in FIG. 4 , the press-fit fixing structure increases the outer diameter of the end portion 28 a of the vane spring 28 , so that only between the end portion 28 a of the vane spring 28 and the cylinder-side spring mounting hole 29 is the cylinder. It is a structure that generates tension in the radial direction of the side spring mounting hole 29 and fixes the vane spring 28 to the cylinder side spring mounting hole 29 by frictional force.

Normally, the high-pressure refrigerant gas in the closed container 10 flows into the back pressure chamber 23b, and the pressure difference between the pressure of the refrigerant gas in the back pressure chamber 23b and the pressure of the refrigerant gas in the cylinder chamber 23a causes the refrigerant gas to move to the center of the cylinder chamber 23a. It creates a force that moves the vanes 26 radially toward them. In the first embodiment, the vane 26 is radially moved toward the center of the cylinder chamber 23a by the force due to the differential pressure between the back pressure chamber 23b and the cylinder chamber 23a and the radial pressing force of the vane spring 28. be The force that moves the vane 26 in the radial direction causes the end of the vane 26 on the side of the cylinder chamber 23 a , ie, the tip of the vane 26 , to contact the cylindrical outer periphery of the rolling piston 22 . Thereby, the space formed by the inner periphery of the cylinder 23 and the outer periphery of the rolling piston 22 can be partitioned. The differential pressure between the pressure of the refrigerant gas in the back pressure chamber 23b and the pressure of the refrigerant gas in the cylinder chamber 23a presses the vane 26 against the outer circumference of the rolling piston 22. As shown in FIG. Therefore, even if the pressure is not sufficient, the force of the vane spring 28 can press the tip of the vane 26 against the outer circumference of the rolling piston 22 . Although the tip of the vane 26 may be temporarily separated from the outer circumference of the rolling piston 22, it can be brought into contact with the outer circumference of the rolling piston 22 again.

As shown in FIG. 1 , an upper bearing 24 that supports the main shaft portion 41 of the crankshaft 40 is arranged on the upper hollow disk surface of the cylinder 23 . A lower bearing 25 that supports the sub shaft portion 43 of the crankshaft 40 is arranged on the hollow disk surface on the lower side of the cylinder 23 . The upper bearing 24 and the lower bearing 25 slidably support the crankshaft 40 .

The upper bearing 24 is fitted to the main shaft portion 41 of the crankshaft 40 to rotatably support the main shaft portion 41, and closes one axial opening of the cylinder chamber 23a. Similarly, the lower bearing 25 is fitted to the secondary shaft portion 43 of the crankshaft 40 to rotatably support the secondary shaft portion 43, and closes one axial opening of the cylinder chamber 23a. The cylinder 23 is provided with a suction port (not shown) for sucking the refrigerant gas into the cylinder chamber 23a from the outside of the sealed container 10, and the upper bearing 24 discharges the compressed refrigerant gas to the outside of the cylinder chamber 23a. A discharge port (not shown) is provided. The upper bearing 24 has an approximately inverted T shape when viewed from the side, and the lower bearing 25 has an approximately T shape when viewed from the side.

A discharge valve (not shown) is provided at the discharge port of the upper bearing 24 to control the discharge timing of the high-temperature, high-pressure refrigerant gas discharged from the cylinder 23 through the discharge port. That is, the discharge valve closes until the refrigerant gas compressed in the cylinder chamber 23a of the cylinder 23 reaches a predetermined pressure, and opens when the pressure exceeds the predetermined pressure to discharge the high-temperature, high-pressure refrigerant gas out of the cylinder chamber 23a. Let

In the cylinder chamber 23a, the operations of suction, compression, and discharge are repeated, so the refrigerant gas discharged from the discharge port is intermittently discharged, resulting in noise such as pulsating noise. In order to reduce this, a discharge muffler 27 is attached to the outside of the upper bearing 24, that is, on the motor 30 side so as to cover the upper bearing 24. As shown in FIG. The discharge muffler 27 is provided with a discharge hole (not shown) that communicates the space formed by the discharge muffler 27 and the upper bearing 24 with the inside of the sealed container 10 . Refrigerant gas discharged from the cylinder 23 through the discharge port is once discharged into the space formed by the discharge muffler 27 and the upper bearing 24, and then discharged into the sealed container 10 through the discharge hole.

A suction muffler 101 is provided on the side of the sealed container 10 to prevent the liquid refrigerant from being directly sucked into the cylinder chamber 23a of the cylinder 23. This suction muffler 101 is fixed to the side surface of the sealed container 10 by welding or the like. In general, the hermetic compressor 100 receives a mixture of low-pressure refrigerant gas and liquid refrigerant from an external refrigerant circuit to which the hermetic compressor 100 is connected. If the liquid refrigerant flows into the cylinder 23 and is compressed by the compression mechanism 20, the compression mechanism 20 will malfunction. send. The suction muffler 101 is connected to the suction port of the cylinder 23 by a suction connecting pipe 21, and the low-pressure refrigerant gas sent from the suction muffler 101 is sucked into the cylinder chamber 23a through the suction connecting pipe 21.

The compression mechanism portion 20 according to Embodiment 1 is configured as described above, and the rotational motion of the crankshaft 40 causes the eccentric shaft portion 42 of the crankshaft 40 to rotate within the cylinder chamber 23 a of the cylinder 23 . A space (hereinafter referred to as a working chamber) partitioned by the inner periphery of the cylinder chamber 23a, the outer periphery of the rolling piston 22 fitted to the eccentric shaft portion 42, and the vane 26 increases and decreases in volume as the crankshaft 40 rotates. do.

First, the working chamber communicates with the intake port, and the low-pressure refrigerant gas sent from the intake muffler 101 is sucked into the working chamber. Next, communication of the suction port is closed, and the refrigerant gas in the working chamber is compressed along with the volume reduction of the working chamber. Finally, the working chamber communicates with the discharge port, and after the refrigerant gas in the working chamber reaches a predetermined pressure, the discharge valve provided at the discharge port opens, and the refrigerant gas is compressed outside the working chamber, i.e., outside the cylinder chamber 23a, to a high pressure. The high temperature refrigerant gas is discharged. The high-pressure and high-temperature refrigerant gas discharged into the closed container 10 from the cylinder chamber 23a through the discharge muffler 27 passes through the electric motor 30, rises in the closed container 10, and reaches the discharge port provided at the top of the closed container 10. It is discharged to the outside of the sealed container 10 from the pipe 102 . A refrigerant circuit through which refrigerant flows is formed outside the sealed container 10 , and the discharged refrigerant circulates through the refrigerant circuit and returns to the suction muffler 101 again.

FIG. 5 is a schematic configuration diagram of a refrigeration cycle device 200 including the hermetic compressor 100 according to Embodiment 1. FIG.

Refrigeration cycle device 200, as shown in FIG. A channel switching valve 103 for switching the flow of refrigerant from the machine 100, an outdoor heat exchanger 104, an expansion device 105 such as an electric expansion device, and an indoor heat exchanger 106 are connected by a refrigerant pipe 201 to circulate the refrigerant. It has a refrigerant circuit that As the refrigerant circulating in the refrigerant circuit, R407C refrigerant, R410A refrigerant, R32 refrigerant, or the like is generally used. In general, in the refrigeration cycle device 200, the indoor heat exchanger 106 is an indoor device, and the remaining hermetic compressor 100, flow path switching valve 103, outdoor heat exchanger 104, and throttle device 105 are outdoors. installed in the device. Also, the refrigeration cycle device 200 according to the embodiment is assumed to be applied to an air conditioner capable of cooling and heating operations.

For example, in the heating operation of the refrigeration cycle device 200, the channel switching valve 103 is connected to the solid line side in FIG. The high-temperature, high-pressure refrigerant compressed by the hermetic compressor 100 flows into the indoor-side heat exchanger 106, where it is condensed and liquefied, and then throttled by the expansion device 105 into a low-temperature, low-pressure two-phase state. The low-temperature, low-pressure two-phase refrigerant flows to the outdoor heat exchanger 104 , evaporates, gasifies, and returns to the hermetic compressor 100 through the flow path switching valve 103 . That is, the refrigerant circulates as indicated by solid line arrows in FIG. Due to this circulation, the outdoor heat exchanger 104, which is an evaporator, exchanges heat with the outside air, and the refrigerant sent to the outdoor heat exchanger 104 absorbs heat. It is sent to the vessel 106 and exchanges heat with the air in the room to warm the air in the room.

Also, in the cooling operation of the refrigeration cycle device 200, the flow path switching valve 103 is connected to the dashed line side in FIG. The high-temperature, high-pressure refrigerant compressed by the hermetic compressor 100 flows to the outdoor heat exchanger 104, where it is condensed and liquefied, and then throttled by the expansion device 105 to become a low-temperature, low-pressure two-phase state. The low-temperature, low-pressure two-phase refrigerant flows to the indoor heat exchanger 106 , evaporates, gasifies, and returns to the hermetic compressor 100 through the flow path switching valve 103 . That is, when the heating operation changes to the cooling operation, the indoor heat exchanger 106 changes from a condenser to an evaporator, and the outdoor heat exchanger 104 changes from an evaporator to a condenser. Therefore, the coolant circulates as indicated by the dashed arrows in FIG. Due to this circulation, the indoor heat exchanger 106, which is an evaporator, exchanges heat with the indoor air, and absorbs heat from the indoor air, that is, cools the indoor air. 104, heat is exchanged with the outside air, and the heat is released to the outside air.

FIG. 6 is a schematic cross-sectional view of the electric motor 30 of the hermetic compressor 100 according to Embodiment 1. FIG. FIG. 6 is a cross-sectional view of the electric motor 30 cut along BB in FIG. 1 and viewed from above.

The electric motor 30 uses electric power supplied from an external power source to generate rotational driving force, and transmits the rotational driving force to the compression mechanism section 20 via the crankshaft 40 . As shown in FIG. 6 , the electric motor 30 includes a hollow cylindrical stator 32 fixed to the inner circumference of the closed container 10 and a cylindrical rotating rotor rotatably arranged inside the inner circumference of the stator 32 . child 31;

The stator 32 includes a stator core 32a in which thin electromagnetic steel plates are stacked in the axial direction of the crankshaft 40, stator windings 37 wound around the stator core 32a, the stator core 32a and the stator windings. and an insulating member (not shown) that insulates the wire 37 .

The rotor 31 is composed of a rotor core 31a formed by stacking core sheets punched from thin electromagnetic steel sheets. The electromagnetic steel sheets forming the rotor core 31a are formed by punching electromagnetic steel sheets into a predetermined shape, stacking multiple sheets in the axial direction of the crankshaft 40, and fixing the stacked electromagnetic steel sheets to each other by caulking or welding.

The configuration of the rotor 31 includes those using permanent magnets, such as brushless DC motors, and those using secondary windings, such as induction motors. When the rotor 31 is, for example, a brushless DC motor as shown in FIG. 6, magnet insertion holes 31c are provided in the axial direction of the rotor core 31a. Permanent magnets 33 such as ferrite magnets or rare earth magnets are inserted into the magnet insertion holes 31c, and the permanent magnets 33 form magnetic poles on the rotor 31. As shown in FIG. The rotor 31 is rotated by the action of the magnetic flux produced by the magnetic poles on the rotor 31 and the magnetic flux produced by the stator windings 37 of the stator 32 .

If the rotor 31 is an induction motor (not shown), the rotor core 31a is provided with a secondary winding instead of a permanent magnet, and the stator winding 37 of the stator 32 is on the rotor side. A magnetic flux is induced in the secondary winding to generate a rotational force to rotate the rotor 31 .

A shaft hole 31b penetrating in the axial direction is provided at the center of the rotor core 31a. A main shaft portion 41 of the crankshaft 40 is inserted into the shaft hole 31b, and the rotary motion of the rotor 31 is transmitted to the crankshaft 40 by fixing the main shaft portion 41 to the rotor 31 by shrink fitting or the like. be done. An air hole 35 is provided around the shaft hole 31 b , and the high-pressure, high-temperature refrigerant compressed by the compression mechanism 20 below the electric motor 30 passes through the air hole 35 . The refrigerant compressed by the compression mechanism 20 passes through the air gap between the rotor 31 and the stator 32 or the gap between the stator windings 37 in addition to the air holes 35 .

FIG. 7 is a sectional force diagram around the vane 26 of the hermetic compressor 100 according to Embodiment 1. FIG. FIG. 8 is a cross-sectional view showing a pressing structure for vanes 26 of hermetic compressor 100 according to the first embodiment. 7 is a view of vanes 26 and their surroundings as seen from above, and FIG. 8 is a view of vanes 26 as seen from the outer peripheral side of cylinder 23. FIG. 7 and 8, the one-dot chain line indicates the lateral center position of the vane 26, and the two-dot chain line indicates the lateral center position of the vane spring 28 and the lateral center position of the load from the vane spring 28, respectively. 8, dotted lines indicate the vertical center position of the vane 26, the vertical center position of the vane spring 28, and the vertical center position of the load by the vane spring 28. As shown in FIG.

As shown in FIG. 7, a load F1 is applied by the vane spring 28 in the reciprocating direction of the vane 26 to the rear side of the vane 26 (hereinafter also referred to as the outer peripheral side of the cylinder 23). In addition, on the tip end side of the vane 26 (hereinafter also referred to as the inner peripheral side of the cylinder 23), due to the pressure difference between the high pressure space and the low pressure space, the direction perpendicular to the reciprocating direction of the vane 26, that is, the discharge pressure side (hereinafter referred to as the high pressure side) side) toward the suction pressure side (hereinafter also referred to as low pressure side). A moment is generated in the vane 26 by the load F2, and the vane 26 rotates while the tip side of the vane 26 tilts from the high pressure side to the low pressure side during operation of the hermetic compressor 100 . In order to alleviate this inclination of the vanes 26, in the hermetic compressor 100 according to the first embodiment, the load center position Osf of the vane springs 28 is set to be greater than the center position Ov of the vanes 26, as shown in FIGS. It has a structure that is close to the low pressure side. Here, the load center position Osf by the vane spring 28 is the center position where the load F1 by the vane spring 28 is applied to the back side of the vane 26 . In this way, a structure in which the load center position Osf of the vane spring 28 is closer to the low pressure side than the center position Ov of the vane 26, that is, the center axis of the vane spring 28 is located on the low pressure side of the center of the vane groove 23c in the cylinder 23. The structure is close to By doing so, the moment caused by the load F1 in the direction of the moment generated by the load F2 can be alleviated rather than the center position Ov of the vane 26, which is the normal load center position, as the load center position Osf of the vane spring 28. can. Note that the center position Osf of the load applied by the vane spring 28 is the same as the center position Os of the vane spring 28, as shown in FIG.

FIG. 9 is a cross-sectional view showing a first modification of the pressing structure of the vanes 26 of the hermetic compressor 100 according to Embodiment 1. As shown in FIG. FIG. 10 is a cross-sectional view showing a second modification of the pressing structure for vanes 26 of hermetic compressor 100 according to the first embodiment. 9 and 10 are views of the vane 26 viewed from the outer peripheral side of the cylinder 23. FIG. 9 and 10, the one-dot chain line indicates the lateral center position of the vane 26, and the two-dot chain line indicates the lateral center position of the sum of the loads of the vane springs 28, respectively. 9 and 10, the dotted line indicates the vertical center position of the vane 26 and the vertical center position of the sum of the loads of the vane springs 28. As shown in FIG.

The hermetic compressor 100 according to Embodiment 1 has a structure in which one vane spring 28 is provided for one vane 26, but the structure is not limited to this. As shown in FIG. 9, a structure in which a plurality of vane springs 28 are provided for one vane 26 may be employed. In this case, the central position of the sum of the loads F1 by the plurality of vane springs 28 (hereinafter also referred to as the combined load central position Osfs) is located on the low pressure side of the vane 26 with respect to the back side of the vane 26 with respect to the central position Ov. The structure should be close to each other. In this way, the structure is such that the combined load center position Osfs of the plurality of vane springs 28 is closer to the low pressure side than the center position Ov of the vanes 26 . By doing so, rather than setting the combined load center position Osfs of the plurality of vane springs 28 to the center position Ov of the vane 26, which is the normal combined load center position, the sum of the loads F1 in the direction of the moment generated by the load F2 Moments can be relaxed.

Further, in the hermetic compressor 100 according to the first embodiment shown in FIG. is closer to the low pressure side, but is not limited thereto. As shown in FIG. 10, a structure in which the central position Os of the vane spring 28 is the same as the central position Ov of the vane 26 and is not located on the low pressure side may be employed. In this case, as shown in FIG. 10, the low-pressure side width Ll of the vane spring 28 is larger than the high-pressure side width Lh (that is, Ll>Lh). The wire diameter is smaller than the wire diameter on the high pressure side. By doing so, the load center position Osf of the vane spring 28 can be shifted from the center position Ov of the vane 26 to the low pressure side.

As described above, the hermetic compressor 100 according to Embodiment 1 includes the hermetic container 10 forming the outer shell and the compression mechanism section 20 housed in the hermetic container 10 . The compression mechanism 20 includes a hollow cylindrical cylinder 23 having vane grooves 23c provided in the radial direction, a rolling piston 22 that rotates eccentrically along the inner peripheral surface of the cylinder 23, and the inside of the vane grooves 23c. A vane 26 that reciprocates and divides the space between the inner peripheral surface of the cylinder 23 and the rolling piston 22 into a high pressure side and a low pressure side, and a vane spring 28 that urges the vane 26 to abut against the rolling piston 22. , is equipped with The load center position Osf of the vane spring 28 is closer to the low pressure side than the center position Ov of the vane 26 .

According to the hermetic compressor 100 according to Embodiment 1, the load center position Osf of the vane spring 28 is closer to the low pressure side than the center position Ov of the vane 26 . Therefore, rather than setting the load center position Osf of the vane spring 28 to the center position Ov of the vane 26, which is the normal load center position, the moment caused by the load F1 in the direction of the moment generated by the load F2 can be reduced. As a result, the inclination of the vane 26 is suppressed, so that the generation of abnormal noise when the vane 26 reciprocates inside the vane groove 23c can be suppressed. can be obtained.

Further, the hermetic compressor 100 according to Embodiment 1 includes a plurality of vane springs 28, and the combined load central position Osfs of the plurality of vane springs 28 is closer to the low pressure side than the central position Ov of the vanes 26.

According to the hermetic compressor 100 according to Embodiment 1, the combined load central position Osfs of the plurality of vane springs 28 is closer to the low pressure side than the central position Ov of the vanes 26 . Therefore, rather than setting the combined load center position Osfs of the plurality of vane springs 28 to the center position Ov of the vane 26, which is the normal combined load center position, the moment generated by the load F2 in the direction of the moment caused by the sum of the loads F1 is relaxed. can do. As a result, the inclination of the vane 26 is suppressed, so that the generation of abnormal noise when the vane 26 reciprocates inside the vane groove 23c can be suppressed. can be obtained.

In the hermetic compressor 100 according to Embodiment 1, the vane spring 28 has a shape in which the outer diameter on the low pressure side is larger than the outer diameter on the high pressure side, or the wire diameter on the low pressure side is the wire diameter on the high pressure side. The shape is smaller than the diameter.

According to the hermetic compressor 100 according to Embodiment 1, even in a structure in which the center position Os of the vane spring 28 is not shifted to the low pressure side, the load center position Osf of the vane spring 28 is set to the center position Ov of the vane 26 . can be shifted to the low pressure side. Therefore, rather than setting the load center position Osf of the vane spring 28 to the center position Ov of the vane 26, which is the normal load center position, the moment caused by the load F1 in the direction of the moment generated by the load F2 can be reduced. As a result, the inclination of the vane 26 is suppressed, so that the generation of abnormal noise when the vane 26 reciprocates inside the vane groove 23c can be suppressed. can be obtained.

Further, the refrigeration cycle apparatus 200 according to Embodiment 1 includes the hermetic compressor 100, the outdoor heat exchanger 104, the expansion device 105, and the indoor heat exchanger 106. .

According to the hermetic compressor 100 according to Embodiment 1, the same effect as the hermetic compressor 100 described above can be obtained.

Embodiment 2.
Embodiment 2 will be described below, but descriptions of parts that overlap with those of Embodiment 1 will be omitted, and parts that are the same as or correspond to those of Embodiment 1 will be given the same reference numerals.

FIG. 11 is a sectional force diagram around the vane 26 of the hermetic compressor 100 according to the second embodiment. FIG. 12 is a diagram showing the shape of vane 26 of hermetic compressor 100 according to the second embodiment. FIG. 11 is a top view of the vane 26 and its surroundings. 12(a) is a plan view of the vane 26, and FIG. 12(b) is a side view of the vane 26 as viewed in the direction of the arrow in FIG. 12(a). Further, in FIG. 11 , the dashed-dotted line indicates the lateral center position of the vane 26 .

In the hermetic compressor 100 according to Embodiment 2, as shown in FIG. 11 , the vane spring 28 is arranged so that the end on the vane 26 side with respect to the reciprocating direction of the vane 26 is on the low pressure side and on the opposite side to the vane 26 . It has a structure in which the end portion 28a is inclined so as to be on the high pressure side. That is, the end 28a of the vane spring 28 opposite to the vane 26 is closer to the high pressure side than the vane 26, and the vane spring 28 extends toward the vane 26 from the high pressure side to the low pressure side. Thus, the vane spring 28 is inclined with respect to the reciprocating direction of the vane 26 . By doing so, a load F3 is generated on the back side of the vane 26 in the direction from the high pressure side to the low pressure side. Since the load F3 is a component that cancels the moment generated in the vane 26 by the load F2, the moment can be suppressed by the load F3.

11, the cylinder-side spring mounting hole 29 of the cylinder 23 is inclined with respect to the reciprocating direction of the vane 26. Another method is to incline the vane spring seating surface 26b of the notch 26a. The vane spring seating surface 26b is a surface to which the vane 26 side end of the vane spring 28 is fixed. Here, the vane spring seating surface 26b is inclined toward the distal end side with respect to the thickness direction of the vane 26 (horizontal direction in the plan view of FIG. 12).

FIG. 13 is a cross-sectional view showing the pressing structure of the vane 26 of the hermetic compressor 100 according to the second embodiment. FIG. 14 is a cross-sectional view showing a first modification of the pressing structure of vanes 26 of hermetic compressor 100 according to the second embodiment.

Instead of forming the vane spring seating surface 26b on the back side of the vane 26 as described above and tilting the vane spring seating surface 26b, as shown in FIG. A mounting hole 26c may be provided. That is, instead of forming the vane spring seating surface 26b on the back side of the vane 26, the vane side spring mounting hole 26c may be provided. When the vane 26 is provided with the vane-side spring mounting hole 26c, the width of the vane 26 is required to correspond to the tilt of the vane spring 28. Therefore, the width of the vane 26 on the back side is made larger than the width on the tip side. It is better to have a structure that

Further, when the vane-side spring mounting hole 26c is provided on the back side of the vane 26, the machining accuracy of the vane spring seating surface 26b is not required. As a structure for fixing to the spring mounting hole 26c, a groove fixing structure or a press-fit fixing structure may be used. In the groove fixing structure, as shown in FIG. 14, the enlarged inner diameter portion is formed by enlarging the inner diameter of the vane-side spring mounting hole 26c in accordance with the outer diameter of the enlarged end of the vane spring 28 on the vane 26 side. The structure is such that the end portion of the vane spring 28 on the vane 26 side is housed in (not shown) to be fixed. In the press-fit fixing structure, by increasing the outer diameter of the end of the vane spring 28 on the vane 26 side, the outer diameter of the end of the vane spring 28 on the vane 26 side and the radial tension of the vane-side spring mounting hole 26c are reduced. Frictional force is generated to fix the vane spring 28 to the vane-side spring mounting hole 26c.

As described above, the hermetic compressor 100 according to the second embodiment includes the hermetic container 10 forming the outer shell and the compression mechanism section 20 housed in the hermetic container 10 . The compression mechanism 20 includes a hollow cylindrical cylinder 23 having vane grooves 23c provided in the radial direction, a rolling piston 22 that rotates eccentrically along the inner peripheral surface of the cylinder 23, and the inside of the vane grooves 23c. A vane 26 that reciprocates and divides the space between the inner peripheral surface of the cylinder 23 and the rolling piston 22 into a high pressure side and a low pressure side, and a vane spring 28 that urges the vane 26 to abut against the rolling piston 22. , is equipped with The vane spring 28 is provided so as to apply a load to the rear side of the vane 26 in the direction from the high pressure side to the low pressure side.

In the hermetic compressor 100 according to the second embodiment, the vane spring 28 is inclined so that the end on the vane 26 side is on the low pressure side and the end 28a on the side opposite to the vane 26 is on the high pressure side. there is

According to the hermetic compressor 100 according to Embodiment 2, a load F3 is generated on the back side of the vane 26 in the direction from the high pressure side to the low pressure side. Since the load F3 is a component that cancels the moment generated in the vane 26 by the load F2, the moment can be suppressed by the load F3. As a result, the inclination of the vane 26 is suppressed, so that the generation of abnormal noise when the vane 26 reciprocates inside the vane groove 23c can be suppressed. can be obtained.

Further, in the hermetic compressor 100 according to Embodiment 2, a vane-side spring mounting hole 26c for fixing the vane spring 28 is provided on the back side of the vane 26 .

According to the hermetic compressor 100 according to the second embodiment, the end of the vane spring 28 on the vane 26 side can be fixed to the vane 26 without forming the vane spring seating surface 26b on the back side of the vane 26. can be done.

Further, the refrigeration cycle apparatus 200 according to Embodiment 2 includes the hermetic compressor 100, the outdoor heat exchanger 104, the expansion device 105, and the indoor heat exchanger 106. .

According to the hermetic compressor 100 according to Embodiment 2, the same effect as the hermetic compressor 100 described above can be obtained.

10 closed container, 11 upper container, 12 lower container, 20 compression mechanism, 21 suction connecting pipe, 22 rolling piston, 23 cylinder, 23a cylinder chamber, 23b back pressure chamber, 23c vane groove, 24 upper bearing, 25 lower bearing, 26 vane, 26a notch, 26b vane spring seating surface, 26c vane side spring mounting hole, 27 discharge muffler, 28 vane spring, 28a end, 29 cylinder side spring mounting hole, 29a inner diameter enlarged portion, 30 electric motor, 31 rotations child, 31a rotor core, 31b shaft hole, 31c magnet insertion hole, 32 stator, 32a stator core, 33 permanent magnet, 35 air hole, 37 stator winding, 40 crankshaft, 41 main shaft, 42 eccentric shaft , 43 auxiliary shaft portion, 100 hermetic compressor, 101 suction muffler, 102 discharge pipe, 103 flow path switching valve, 104 outdoor heat exchanger, 105 throttle device, 106 indoor heat exchanger, 200 refrigeration cycle device, 201 Refrigerant piping.

Claims

a closed container forming an outer shell;
and a compression mechanism housed in the sealed container,
The compression mechanism section is
a hollow cylindrical cylinder having radial vane grooves;
a rolling piston that rotates eccentrically along the inner peripheral surface of the cylinder;
a vane that reciprocates inside the vane groove and divides the space between the inner peripheral surface of the cylinder and the rolling piston into a high pressure side and a low pressure side;
a vane spring that biases the vane to abut against the rolling piston;
A hermetic compressor, wherein the load center position of the vane spring is closer to the low pressure side than the center position of the vane.
comprising a plurality of said vane springs,
2. The hermetic compressor according to claim 1, wherein a center position of combined load by said plurality of vane springs is closer to a low pressure side than a center position of said vane.
The vane spring is
The hermetic compressor according to claim 1, wherein the width of the low pressure side is wider than the width of the high pressure side.
The vane spring is
The hermetic compressor according to claim 1, wherein the wire diameter on the low pressure side is smaller than the wire diameter on the high pressure side.
a closed container forming an outer shell;
and a compression mechanism housed in the sealed container,
The compression mechanism section is
a hollow cylindrical cylinder having radial vane grooves;
a rolling piston that rotates eccentrically along the inner peripheral surface of the cylinder;
a vane that reciprocates inside the vane groove and divides the space between the inner peripheral surface of the cylinder and the rolling piston into a high pressure side and a low pressure side;
a vane spring that biases the vane to abut against the rolling piston;
The hermetic compressor, wherein the vane spring is provided so as to apply a load to the rear side of the vane in a direction from a high pressure side to a low pressure side.
The vane spring is
6. The hermetic compressor according to claim 5, wherein the vane-side end is inclined to the low pressure side and the end opposite to the vane is inclined to the high pressure side.
On the back side of the vane,
The hermetic compressor according to any one of claims 1 to 6, further comprising a vane-side spring mounting hole for fixing the vane spring.
The vane is
8. The hermetic compressor according to claim 7, wherein the width on the back side is larger than the width on the tip side.
The hermetic compressor according to claim 7 or 8, wherein the vane is fixed to the vane-side spring mounting hole by a press-fit fixing structure.
The hermetic compressor according to claim 7 or 8, wherein the vane is fixed to the vane-side spring mounting hole by a groove fixing structure.
A hermetic compressor according to any one of claims 1 to 10;
an outdoor heat exchanger;
a diaphragm device;
A refrigeration cycle device comprising: an indoor heat exchanger.