Compressor and refrigeration cycle device

Abstract

This compressor comprises a compression mechanism and a sealed container. The compression mechanism includes: a hollow cylindrical cylinder that is fixed to the inner circumferential surface of the sealed container by thermal caulking or welding and has a vane groove; a rolling piston that eccentrically rotates along the inner circumferential surface of the cylinder; and a vane that reciprocates in the vane groove and partitions a space between the inner circumferential surface of the cylinder and the rolling piston. The cylinder has formed therein a plurality of circular arc holes that extend in a circular arc shape along the circumferential direction of the cylinder, and that penetrate the cylinder in the axial direction of the cylinder. The cylinder has a bridge part formed between two circular arc holes adjacent to each other in the circumferential direction, among the plurality of circular arc holes. When a straight line that extends along the radial direction of the cylinder from the center axis of the cylinder toward the bridge part is defined as a radial direction line, and a straight line that obliquely intersects the radial direction line in the bridge part is defined as an intersection straight line, the bridge part is formed in a manner so as to extend along the intersection straight line.

Description

Compressor and refrigeration cycle device

[0001] The present disclosure relates to a compressor and a refrigeration cycle device including the compressor.

[0002] Patent Document 1 describes a rotary compressor. The rotary compressor includes a sealed housing and a rotary compression mechanism installed within the housing. The rotary compression mechanism is driven via a crankshaft connected to a drive source. The rotary compression mechanism includes a cylinder body defining a cylinder chamber, upper and lower bearings installed on the upper and lower surfaces of the cylinder body to support the crankshaft, and a rotor fitted to an eccentric portion of the crankshaft and rotating within the cylinder chamber. The upper bearing, cylinder body, and lower bearing are integrated by fastening a bolt that passes through the crankshaft in the axial direction.

[0003] Japanese Patent Application Laid-Open No. 2015-175273

[0004] In the rotary compressor described above, when the cylinder body is fixed to the inner peripheral surface of the housing by welding or thermal caulking, the heat generated during the fixing process generates stress in the cylinder body in the radial direction, which results in distortion of the inner peripheral surface of the cylinder and a decrease in the roundness of the inner peripheral surface of the cylinder.

[0005] The present disclosure has been made to solve the above-mentioned problems, and aims to provide a compressor and a refrigeration cycle device that can suppress distortion of the inner circumferential surface of the cylinder.

[0006] A compressor according to the present disclosure includes a compression mechanism that compresses a refrigerant, and a sealed container that houses the compression mechanism. The compression mechanism includes a hollow cylindrical cylinder that is fixed to an inner peripheral surface of the sealed container by thermal caulking or welding and has a vane groove, a rolling piston that rotates eccentrically along the inner peripheral surface of the cylinder, and a vane that reciprocates inside the vane groove and separates a space between the inner peripheral surface of the cylinder and the rolling piston. The cylinder is formed with a plurality of arc holes that extend in an arc shape along the circumferential direction of the cylinder and penetrate the cylinder in the axial direction of the cylinder. The cylinder has a bridge portion that is formed between two of the plurality of arc holes that are adjacent to each other in the circumferential direction. When a radial line is defined as a line extending radially from a central axis of the cylinder toward the bridge portion, and a line that obliquely intersects the radial line at the bridge portion is defined as an intersecting line, the bridge portion is formed to extend along the intersecting line.

[0007] A refrigeration cycle device according to the present disclosure includes a compressor according to the present disclosure, an outdoor heat exchanger, a pressure reducer, and an indoor heat exchanger.

[0008] According to the present disclosure, distortion of the inner peripheral surface of the cylinder can be suppressed.

[0009] 5 is a cross-sectional view showing the configuration of a compressor according to embodiment 1. FIG. 6 is a schematic cross-sectional view showing the II-II cross section of FIG. 1. FIG. 7 is a schematic configuration diagram of a refrigeration cycle device according to embodiment 1. FIG. 8 is a cross-sectional view showing the IV-IV cross section of FIG. 1. FIG. 9 is a schematic top view showing the configuration of a cylinder of a compressor according to embodiment 1. FIG. 10 is a schematic cross-sectional view showing the VI-VI cross section of FIG. 5. FIG. 11 is a schematic cross-sectional view showing the configuration of a cylinder of a compressor according to embodiment 2. FIG. 12 is a schematic top view showing the configuration of a cylinder of a compressor according to embodiment 3.

[0010] Embodiments of the present disclosure will be described below with reference to the drawings. The present disclosure is not limited to the following embodiments and can be modified in various ways without departing from the spirit and scope of the present disclosure. Furthermore, the present disclosure includes all possible combinations of the configurations shown in the following embodiments. In particular, the combinations of components are not limited to those in each embodiment; components described in one embodiment can be applied to another embodiment. In the following description, directional terms (e.g., "up," "down," "right," "left," "front," "rear," etc.) are used as appropriate to facilitate understanding, but these are for explanatory purposes and do not limit the present disclosure. In each drawing, components designated with the same reference numerals are identical or equivalent, and this applies throughout the entire specification. Note that the relative dimensional relationships or shapes of each component in each drawing may differ from those in reality.

[0011] Embodiment 1 A compressor and a refrigeration cycle apparatus according to embodiment 1 will be described. Fig. 1 is a cross-sectional view showing the configuration of a compressor according to this embodiment. In this embodiment, a one-cylinder rotary compressor is exemplified as the compressor.

[0012] As shown in Fig. 1, the compressor 100 includes a compression mechanism 20 that compresses refrigerant gas, an electric motor 30 that drives the compression mechanism 20, and a sealed container 10 that houses the compression mechanism 20 and the electric motor 30. The sealed container 10 includes an upper container 11 and a lower container 12. The compression mechanism 20 is disposed in a lower portion of the sealed container 10. The electric motor 30 is disposed above the compression mechanism 20 within the sealed container 10.

[0013] The compression mechanism 20 and the electric motor 30 are connected by a rotating shaft 21. The rotating shaft 21 transmits the rotational motion of the electric motor 30 to the compression mechanism 20. The compression mechanism 20 compresses refrigerant gas using the transmitted rotational force and discharges it into the sealed container 10. The inside of the sealed container 10 is filled with compressed, high-temperature, high-pressure refrigerant gas. Refrigerant oil for lubricating the compression mechanism 20 is stored at the bottom of the sealed container 10. An oil pump (not shown) is provided below the rotating shaft 21. As the rotating shaft 21 rotates, the oil pump draws up refrigerant oil from the bottom of the sealed container 10 and supplies it to each sliding part of the compression mechanism 20. This ensures mechanical lubrication of the compression mechanism 20.

[0014] The rotating shaft 21 has a main shaft portion 21a, an eccentric shaft portion 21b, and a counter shaft portion 21c. The main shaft portion 21a, the eccentric shaft portion 21b, and the counter shaft portion 21c are arranged in this order along the axial direction of the rotating shaft 21. An electric motor 30 is fixed to the main shaft portion 21a by shrink fitting or press fitting. A cylindrical rolling piston 22 is slidably fitted to the eccentric shaft portion 21b.

[0015] Figure 2 is a schematic cross-sectional view showing the II-II cross section of Figure 1. In Figure 2, suction ports, discharge ports, etc. are omitted from the illustration. In the following description, the direction along the central axis L1 of the cylinder 23 may be referred to as the "axial direction of the cylinder" or simply as the "axial direction." In a cross section perpendicular to the axial direction, the direction along the circumference of a circle centered on the central axis L1 of the cylinder 23 may be referred to as the "circumferential direction of the cylinder" or simply as the "circumferential direction." In the same cross section, the direction along the radius of the cylinder 23 may be referred to as the "radial direction of the cylinder" or simply as the "radial direction."

[0016] 2 and 1, the compression mechanism 20 includes a cylinder 23, a rolling piston 22, an upper bearing 24, a lower bearing 25, and a vane 26. The cylinder 23 is formed in a hollow cylindrical shape. A cylindrical space, i.e., a cylinder chamber 23a, which is open at both axial ends, is provided inside the cylinder 23.

[0017] The cylinder chamber 23a accommodates the eccentric shaft portion 21b, the rolling piston 22, and the vane 26. The eccentric shaft portion 21b performs eccentric rotation within the cylinder chamber 23a as the rotary shaft 21 rotates. The rolling piston 22 is fitted onto the outer periphery of the eccentric shaft portion 21b. The space formed by the inner circumferential surface of the cylinder 23 and the outer circumferential surface of the rolling piston 22 is partitioned by the vane 26.

[0018] A vane groove 23c is formed in the cylinder 23. One end of the vane groove 23c opens into the cylinder chamber 23a. A back pressure chamber 23b is provided at the other end of the vane groove 23c. A vane 26 is housed in the vane groove 23c. The vane 26 reciprocates within the vane groove 23c along the radial direction of the cylinder 23. The shape of the vane 26 is approximately rectangular parallelepiped. When the vane 26 is attached to the vane groove 23c, the thickness of the vane 26 along the circumferential direction of the cylinder 23 is smaller than the length of the vane 26 along the radial direction of the cylinder 23 and the height of the vane 26 along the axial direction of the cylinder 23.

[0019] A vane spring (not shown) is provided in the back pressure chamber 23b of the vane groove 23c. Normally, high-pressure refrigerant gas in the sealed container 10 flows into the back pressure chamber 23b. 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 generates a force that pushes the vane 26 radially toward the center of the cylinder chamber 23a. The force due to this pressure difference and the force of the vane spring pushing the vane 26 radially push the vane 26 radially toward the center of the cylinder chamber 23a. One end of the vane 26, i.e., the end on the cylinder chamber 23a side, abuts against the outer peripheral surface of the rolling piston 22 due to these forces. As a result, the space formed by the inner peripheral surface of the cylinder 23 and the outer peripheral surface of the rolling piston 22 is divided into a high-pressure side and a low-pressure side by the vane 26. Even if the pressure difference between the refrigerant gas in the back pressure chamber 23b and the refrigerant gas in the cylinder chamber 23a is not sufficient, the force of the vane spring presses one end of the vane 26 against the outer circumferential surface of the rolling piston 22. Therefore, one end of the vane 26 can be kept in contact with the outer circumferential surface of the rolling piston 22 at all times.

[0020] The upper bearing 24 is fitted onto the main shaft portion 21 a of the rotary shaft 21 and rotatably supports the main shaft portion 21 a. The upper bearing 24 also closes one axial opening of the cylinder chamber 23 a. The upper bearing 24 has a substantially inverted T-shape in side view.

[0021] The lower bearing 25 is fitted onto the countershaft portion 21c of the rotary shaft 21 and rotatably supports the countershaft portion 21c. The lower bearing 25 also closes the other axial opening of the cylinder chamber 23a. The lower bearing 25 is substantially T-shaped in side view.

[0022] The cylinder 23 is provided with a suction port (not shown) that draws refrigerant gas into the cylinder chamber 23a from outside the sealed container 10. The upper bearing 24 is provided with a discharge port (not shown) that discharges the compressed refrigerant gas to the outside of the cylinder chamber 23a.

[0023] A discharge valve (not shown) is provided in the discharge port of the upper bearing 24. The discharge valve controls the timing of refrigerant gas discharge. That is, the discharge valve is closed until the pressure of the refrigerant gas in the cylinder chamber 23a rises to a predetermined pressure. When the pressure of the refrigerant gas in the cylinder chamber 23a rises above the predetermined pressure, the discharge valve is opened, and high-temperature, high-pressure refrigerant gas is discharged to the outside of the cylinder chamber 23a through the discharge port.

[0024] Because the suction, compression, and discharge operations are repeated in the cylinder chamber 23a, the refrigerant gas is intermittently discharged from the discharge port. This can cause noise such as pulsating sounds. To reduce noise, a discharge muffler 27 is attached to the outside of the upper bearing 24, i.e., on the motor 30 side of the upper bearing 24, so as to cover the upper bearing 24. The discharge muffler 27 has a discharge hole. The discharge hole connects the space formed by the discharge muffler 27 and the upper bearing 24 with the space inside the sealed container 10. The refrigerant gas compressed in the cylinder chamber 23a passes through the discharge port and is first discharged into the space formed by the discharge muffler 27 and the upper bearing 24, and then discharged from the discharge hole into the sealed container 10.

[0025] A suction muffler 101 is provided on the side of the sealed container 10. The suction muffler 101 is provided on the suction side of the compressor 100 to prevent liquid refrigerant from being directly drawn into the cylinder chamber 23a. Generally, a mixture of low-pressure refrigerant gas and liquid refrigerant is sent to the compressor 100 from an external refrigerant circuit. If the liquid refrigerant flows into the cylinder chamber 23a and is compressed by the compression mechanism 20, it may cause a malfunction of the compression mechanism 20. For this reason, the suction muffler 101 separates the liquid refrigerant from the refrigerant gas, and only the refrigerant gas is sent to the cylinder chamber 23a. The suction muffler 101 is connected to the suction port of the cylinder 23 by a suction connecting pipe 101a. The low-pressure refrigerant gas sent from the suction muffler 101 is drawn into the cylinder chamber 23a via the suction connecting pipe 101a.

[0026] In the compression mechanism 20, the rotational motion of the rotary shaft 21 causes the eccentric shaft portion 21b to rotate within the cylinder chamber 23a. This causes the rolling piston 22 to rotate eccentrically along the inner circumferential surface of the cylinder 23. The volume of the working chamber, defined by the inner circumferential surface of the cylinder 23, the outer circumferential surface of the rolling piston 22, and the vane 26, increases or decreases as the eccentric shaft portion 21b rotates. First, the working chamber communicates with the suction port, and low-pressure refrigerant gas is drawn into the working chamber. Next, the suction port closes, reducing the volume of the working chamber and compressing the refrigerant gas within the working chamber. Next, the working chamber communicates with the discharge port. When the pressure of the refrigerant gas within the working chamber reaches a predetermined pressure, the discharge valve opens, and the compressed refrigerant gas is discharged to the outside of the cylinder chamber 23a.

[0027] The high-temperature, high-pressure refrigerant gas discharged from the cylinder chamber 23a into the sealed container 10 through the discharge muffler 27 passes through the motor 30 and rises inside the sealed container 10. The high-temperature, high-pressure refrigerant gas is discharged to the outside of the sealed container 10 from a discharge pipe 102 provided at the top of the sealed container 10. The refrigerant discharged from the compressor 100 circulates through the refrigerant circuit and returns to the suction muffler 101.

[0028] FIG. 3 is a schematic diagram of a refrigeration cycle apparatus according to this embodiment. The refrigeration cycle apparatus according to this embodiment is used in refrigeration and air conditioning apparatuses such as air conditioners and refrigerators. As shown in FIG. 3 , the refrigeration cycle apparatus 200 has a refrigeration circuit in which a compressor 100, a four-way switching valve 103, an outdoor heat exchanger 104, a pressure reducer 105 such as an electric expansion valve, and an indoor heat exchanger 106 are connected in sequence via piping. The four-way switching valve 103 is connected to the discharge side of the compressor 100 and is configured to switch the flow of refrigerant. Generally, in refrigeration and air conditioning apparatuses such as air conditioners, the indoor heat exchanger 106 is installed in an indoor unit, and the compressor 100, the four-way switching valve 103, the outdoor heat exchanger 104, and the pressure reducer 105 are installed in an outdoor unit.

[0029] For example, during heating operation of the air conditioner, the four-way selector valve 103 is switched to form the flow path shown by the solid lines in Figure 3. High-temperature, high-pressure refrigerant gas compressed by the compressor 100 passes through the four-way selector valve 103 and flows into the indoor heat exchanger 106. The refrigerant gas that flows into the indoor heat exchanger 106 condenses and liquefies through heat exchange with the indoor air, becoming liquid refrigerant. The liquid refrigerant that flows out of the indoor heat exchanger 106 is throttled by the pressure reducer 105, becoming a low-temperature, low-pressure two-phase refrigerant, and flows into the outdoor heat exchanger 104. The two-phase refrigerant that flows into the outdoor heat exchanger 104 evaporates and gasifies through heat exchange with the outdoor air, becoming refrigerant gas. The refrigerant gas that flows out of the outdoor heat exchanger 104 passes through the four-way selector valve 103 and returns to the suction muffler 101 of the compressor 100. That is, the refrigerant circulates through the refrigerant circuit as shown by the solid arrows in Figure 3. As the refrigerant circulates, the refrigerant absorbs heat from the outdoor air in the outdoor heat exchanger 104, which serves as an evaporator. In the indoor heat exchanger 106, which serves as a condenser, the indoor air is warmed by the heat released from the refrigerant.

[0030] During cooling operation of the air conditioner, the four-way selector valve 103 is switched to form the flow path shown by the dashed lines in Figure 3. High-temperature, high-pressure refrigerant gas compressed by the compressor 100 passes through the four-way selector valve 103 and flows into the outdoor heat exchanger 104. The refrigerant gas that flows into the outdoor heat exchanger 104 condenses and liquefies through heat exchange with outdoor air, becoming liquid refrigerant. The liquid refrigerant that flows out of the outdoor heat exchanger 104 is throttled by the pressure reducer 105, becoming a low-temperature, low-pressure two-phase refrigerant, and flows into the indoor heat exchanger 106. The two-phase refrigerant that flows into the indoor heat exchanger 106 evaporates and gasifies through heat exchange with indoor air, becoming refrigerant gas. The refrigerant gas that flows out of the indoor heat exchanger 106 passes through the four-way selector valve 103 and returns to the suction muffler 101 of the compressor 100. In other words, the refrigerant circulates through the refrigerant circuit as shown by the dashed arrows in Figure 3. When the operation mode changes from heating to cooling, 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. As the refrigerant circulates, the refrigerant absorbs heat from the indoor air in the indoor heat exchanger 106, which functions as an evaporator, thereby cooling the indoor air. In the outdoor heat exchanger 104, which functions as a condenser, the refrigerant releases heat to the outdoor air.

[0031] Examples of the refrigerant include a fluorine-based refrigerant or a hydrocarbon-based refrigerant with a low global warming potential (GWP). Examples of the refrigerant include a single refrigerant selected from R1234yf, R1234ze, R32, and R290, or a mixed refrigerant containing at least one of R1234yf, R1234ze, R32, and R290. This mixed refrigerant may be a mixed refrigerant containing two or more of R1234yf, R1234ze, R32, and R290, or a mixed refrigerant containing at least one of R1234yf, R1234ze, R32, and R290 and another refrigerant. Examples of the refrigerant include a mixed refrigerant containing R1132(E) or a mixed refrigerant containing R1123. Examples of refrigerants include mixed refrigerants such as R516A, R410A, R445A, R444A, R454C, R444B, R454A, R455A, R457A, R459B, R452B, R454B, R447B, R447A, R446A, and R459A.

[0032] Next, the electric motor 30 that transmits rotational force to the compression mechanism 20 will be described. Figure 4 is a cross-sectional view showing a cross section taken along line IV-IV in Figure 1. As shown in Figure 4, the electric motor 30 includes a substantially cylindrical stator 41 fixed to the inner periphery of the sealed container 10, and a substantially columnar rotor 31 disposed inside the stator 41.

[0033] The rotor 31 has a rotor core 32. The rotor core 32 is formed by laminating iron core sheets punched from thin electromagnetic steel plates. Rotor configurations include those that use permanent magnets, as in brushless DC motors, and those that use secondary windings, as in induction motors. For example, in the case of a brushless DC motor as shown in FIG. 4, magnet insertion holes 33 are provided along the axial direction of the rotor core 32. Permanent magnets 34, such as ferrite magnets or rare earth magnets, are inserted into the magnet insertion holes 33. The permanent magnets 34 form magnetic poles on the rotor 31. The rotor 31 rotates due to the interaction between the magnetic flux generated by the magnetic poles on the rotor 31 and the magnetic flux generated by the stator windings of the stator 41.

[0034] Although not shown, in the case of an induction motor, a secondary winding is provided in place of a permanent magnet on the rotor core 32. The stator winding of the stator 41 induces magnetic flux in the secondary winding of the rotor 31, generating a torque that causes the rotor 31 to rotate.

[0035] A shaft hole through which the rotating shaft 21 passes is provided at the center of the rotor core 32. The main shaft portion 21a of the rotating shaft 21 is fixed in this shaft hole by shrink fitting or the like. This allows the rotational motion of the rotor 31 to be transmitted to the rotating shaft 21.

[0036] Air holes 35 are provided around the axial hole. The high-temperature, high-pressure refrigerant gas compressed by the compression mechanism 20 passes through the air holes 35 and rises inside the sealed container 10. In addition to the air holes 35, the high-temperature, high-pressure refrigerant gas compressed by the compression mechanism 20 also passes through the air gap between the rotor 31 and the stator 41 and the gaps in the stator windings.

[0037] Next, a description will be given of essential parts of the compressor 100 according to this embodiment. FIG. 5 is a schematic top view showing the configuration of the cylinder of the compressor according to this embodiment. FIG. 5 shows the configuration of the cylinder 23 as viewed along the axial direction. FIG. 6 is a schematic cross-sectional view showing the VI-VI section of FIG. 5. The cross section shown in FIG. 6 is a plane passing through the central axis L1 of the cylinder 23 and a bridge portion 51-1, which will be described later. The up-down direction in FIG. 6 represents the axial direction of the cylinder 23. The left-right direction in FIG. 6 represents the radial direction of the cylinder 23. In this embodiment, the cylinder 23 is fixed to the inner circumferential surface of the sealed container 10 by thermal caulking or welding.

[0038] 5 and 6 , the cylinder 23 has a first axial end face 23d facing one axial direction and a second axial end face 23e facing the other axial direction. A plurality of arc holes 50 are formed in the radially outer portion of the cylinder 23. Each of the arc holes 50 extends in an arc shape along the circumferential direction of the cylinder 23. Each of the arc holes 50 penetrates the cylinder 23 in the axial direction of the cylinder 23. The multiple arc holes 50 are arranged, for example, on the same circumference centered on the central axis L1 of the cylinder 23.

[0039] The cylinder 23 has a plurality of bridge portions 51-1, 51-2, and 51-3. Each of the bridge portions 51-1, 51-2, and 51-3 is formed between two adjacent arc holes 50 in the circumferential direction of the cylinder 23. In the example shown in Fig. 5, three bridge portions 51-1, 51-2, and 51-3 are provided. The following describes the bridge portion 51-1, but the other bridge portions 51-2 and 51-3 have the same configuration.

[0040] Here, a straight line extending from the central axis L1 of the cylinder 23 toward the bridge portion 51-1 in the radial direction of the cylinder 23 is defined as a radial line L2. The radial line L2 is included in the plane of the cross section shown in FIG. 6. Furthermore, a straight line that diagonally intersects with the radial line L2 at the bridge portion 51-1 is defined as an intersecting line L3. The intersecting line L3 is included in the plane of the cross section shown in FIG. 6. In this case, the bridge portion 51-1 is formed to extend along the intersecting line L3. In other words, the bridge portion 51-1 is formed to extend diagonally with respect to the radial line L2 in a cross section that passes through the central axis L1 of the cylinder 23 and the bridge portion 51-1 and is parallel to the central axis L1.

[0041] The side surface of the bridge portion 51-1 on the first axial end face 23d side is defined as a first surface 52. The surface connecting the outer end 52a of the first surface 52 and the first axial end face 23d in the radial direction of the cylinder 23 is defined as a second surface 53. The side surface of the bridge portion 51-1 on the second axial end face 23e side is defined as a third surface 54. The surface connecting the inner end 54a of the third surface 54 and the second axial end face 23e in the radial direction of the cylinder 23 is defined as a fourth surface 55. The first surface 52 and the second surface 53 are formed so that the distance between them increases as they approach the first axial end face 23d. The third surface 54 and the fourth surface 55 are formed so that the distance between them increases as they approach the second axial end face 23e. The first surface 52, the second surface 53, the third surface 54, and the fourth surface 55 are all inclined with respect to the central axis L1. The first surface 52 and the second surface 53 are inclined relative to the central axis L1 so as to face one axial side, i.e., the first axial end surface 23d side, and the third surface 54 and the fourth surface 55 are inclined relative to the central axis L1 so as to face the other axial side, i.e., the second axial end surface 23e side.

[0042] 6, the length of the bridge portion 51-1 in the direction perpendicular to the intersecting line L3 is defined as T1. The length of the cylinder 23 in the axial direction of the cylinder 23 is defined as T2. In this case, the length T1 is shorter than the length T2 (T1<T2).

[0043] 5, the length a1 of the bridge portion 51-1 in the circumferential direction of the cylinder 23 is shorter than the length a2 of the arc-shaped hole 50 in the circumferential direction of the cylinder 23 (a1<a2). Here, the length a2 is the length of at least one of the multiple arc-shaped holes 50.

[0044] Of the plurality of bridge portions 51-1, 51-2, and 51-3, the two bridge portions 51-1 and 51-2 are disposed at positions facing each other across the central axis L1.

[0045] In the compressor 100 having these configurations, the entire circumference of the inner circumferential surface of the sealed container 10 abuts against the entire circumference of the outer circumferential surface of the cylinder 23, and the sealed container 10 applies a force that causes the outer circumferential surface of the cylinder 23 to contract. In this embodiment, if the cylinder 23 is distorted due to the heat influence during thermal caulking or welding, the bridge portions 51-1, 51-2, and 51-3 deform, thereby suppressing distortion of the inner circumferential surface of the cylinder 23.

[0046] Taking the bridge portion 51-1 as an example, the bridge portion 51-1 is formed to extend along an intersecting line L3. The intersecting line L3 passes through the central axis L1 and the bridge portion 51-1 and obliquely intersects with the radial line L2 in a cross section parallel to the central axis L1. Therefore, even if the bridge portion 51-1 is distorted and deformed due to the influence of heat, the stress generated in the bridge portion 51-1 is resolved into a component in the radial direction of the cylinder 23 and a component in the axial direction of the cylinder 23. This reduces the stress in the radial direction.

[0047] Therefore, distortion of the cylinder 23 that causes the inner peripheral surface of the cylinder 23 to move in the circumferential or radial direction is unlikely to occur. As a result, distortion of the inner peripheral surface of the cylinder 23 that causes the vane grooves 23c to move in the circumferential direction of the cylinder 23 or that causes the groove width of the vane grooves 23c to change can be suppressed. Here, distortion of the cylinder 23 that causes the inner peripheral surface of the cylinder 23 to move in the axial direction may occur. However, compared to distortion of the cylinder 23 in the circumferential and radial directions, distortion of the cylinder 23 in the axial direction is acceptable.

[0048] In this embodiment, the length T1 of the bridge portion 51-1 in the direction perpendicular to the intersecting line L3 is shorter than the length T2 of the cylinder 23 in the axial direction. This makes the bridge portion 51-1 more susceptible to deformation, further suppressing distortion of the inner circumferential surface of the cylinder 23.

[0049] Furthermore, in this embodiment, the first surface 52 and the second surface 53 are formed with draft angles for use in molding the cylinder 23 by casting. Similarly, the third surface 54 and the fourth surface 55 are formed with draft angles for use in molding the cylinder 23 by casting. This allows the cylinder 23 to be suitably molded by casting.

[0050] The length a1 of the bridge portion 51-1 in the circumferential direction of the cylinder 23 is shorter than the length a2 of the arc-shaped hole 50 in the circumferential direction of the cylinder 23. Therefore, compared to when the length a1 of the bridge portion 51-1 is longer than the length a2 of the arc-shaped hole 50, deformation of the bridge portion 51-1 is easier when the cylinder 23 is distorted due to the thermal effects of thermal caulking or welding. Therefore, distortion of the inner circumferential surface of the cylinder 23 can be more reliably suppressed.

[0051] At least one pair of bridge portions 51-1, 51-2 are arranged in positions facing each other across the central axis L1. Therefore, if the cylinder 23 is distorted due to the heat caused by thermal caulking or welding, the pair of bridge portions 51-1, 51-2 tend to deform evenly. This makes it possible to more reliably suppress distortion of the inner peripheral surface of the cylinder 23.

[0052] As described above, the compressor 100 according to this embodiment includes the compression mechanism 20 that compresses a refrigerant and the sealed container 10 that houses the compression mechanism 20. The compression mechanism 20 includes a hollow cylindrical cylinder 23, a rolling piston 22, and a vane 26. The cylinder 23 is fixed to the inner circumferential surface of the sealed container 10 by thermal caulking or welding. The cylinder 23 has a vane groove 23c. The rolling piston 22 rotates eccentrically along the inner circumferential surface of the cylinder 23. The vane 26 reciprocates within the vane groove 23c, and partitions the space between the inner circumferential surface of the cylinder 23 and the rolling piston 22.

[0053] A plurality of arc-shaped holes 50 are formed in the cylinder 23. Each of the arc-shaped holes 50 extends in an arc shape along the circumferential direction of the cylinder 23 and penetrates the cylinder 23 in the axial direction of the cylinder 23. The cylinder 23 has a bridge portion 51-1 formed between two of the arc-shaped holes 50 that are adjacent to each other in the circumferential direction. The bridge portion 51-1 is an example of a bridge portion. A straight line extending along the radial direction of the cylinder 23 from the central axis L1 of the cylinder 23 toward the bridge portion 51-1 is defined as a radial line L2. A straight line that obliquely intersects the radial line L2 at the bridge portion 51-1 is defined as an intersecting line L3. In this case, the bridge portion 51-1 is formed to extend along the intersecting line L3.

[0054] According to this configuration, when the cylinder 23 is fixed to the inner surface of the sealed container 10 by thermal crimping or welding, if the cylinder 23 is distorted due to thermal influence, the bridge portion 51-1 can deform, thereby suppressing distortion of the inner surface of the cylinder 23.

[0055] In the compressor 100 according to the present embodiment, in a cross section passing through the central axis L1 and the bridge portion 51-1 and parallel to the central axis L1, the intersecting line L3 intersects the radial line L2 obliquely.

[0056] With this configuration, when the cylinder 23 is distorted due to the influence of heat, distortion that causes the inner peripheral surface of the cylinder 23 to move in the circumferential or radial direction is less likely to occur, which makes it possible to suppress distortion of the inner peripheral surface of the cylinder 23 that causes the vane grooves 23c to move in the circumferential direction of the cylinder 23 or that changes the groove width of the vane grooves 23c.

[0057] In the compressor 100 according to this embodiment, in the cross section, the length T1 of the bridge portion 51-1 in the direction perpendicular to the intersecting line L3 is shorter than the length T2 of the cylinder 23 in the axial direction.

[0058] According to this configuration, when the cylinder 23 is distorted due to the influence of heat, the bridge portion 51-1 is more likely to deform, so that distortion of the inner peripheral surface of the cylinder 23 can be further suppressed.

[0059] In the compressor 100 according to this embodiment, the cylinder 23 has a first axial end face 23d facing one axial direction and a second axial end face 23e facing the other axial direction. The side of the bridge portion 51-1 on the first axial end face 23d side is defined as a first surface 52. A surface connecting the outer end 52a of the first surface 52 to the first axial end face 23d in the radial direction is defined as a second surface 53. The side of the bridge portion 51-1 on the second axial end face 23e side is defined as a third surface 54. A surface connecting the inner end 54a of the third surface 54 to the second axial end face 23e in the radial direction is defined as a fourth surface 55. In this case, the first surface 52 and the second surface 53 are formed so that the distance between them increases as they approach the first axial end face 23d. The third surface 54 and the fourth surface 55 are formed so that the distance between them increases as they approach the second axial end face 23e. The first surface 52, the second surface 53, the third surface 54, and the fourth surface 55 are all inclined with respect to the central axis L1.

[0060] According to this configuration, a draft is formed on each of the first surface 52, the second surface 53, the third surface 54, and the fourth surface 55. This allows the cylinder 23 to be suitably formed by casting.

[0061] In the compressor 100 according to this embodiment, the length of the bridge portion 51-1 in the circumferential direction is shorter than the length of the arc hole 50 in the circumferential direction.

[0062] According to this configuration, when the cylinder 23 is distorted due to the influence of heat, the bridge portion 51-1 is more likely to deform, so that distortion of the inner peripheral surface of the cylinder 23 can be further suppressed.

[0063] In the compressor 100 according to this embodiment, the bridge portion has a plurality of bridge portions 51-1, 51-2, and 51-3. Of the plurality of bridge portions 51-1, 51-2, and 51-3, two bridge portions 51-1 and 51-2 are arranged in positions facing each other across the central axis L1.

[0064] According to this configuration, when the cylinder 23 is distorted due to the influence of heat, the two bridge portions 51-1, 51-2 tend to deform evenly, so that distortion of the inner peripheral surface of the cylinder 23 can be further suppressed.

[0065] In compressor 100 according to the present embodiment, the refrigerant may be a single refrigerant selected from the group consisting of R1234yf, R1234ze, R32, and R290; a mixed refrigerant containing one or more of R1234yf, R1234ze, R32, and R290; a mixed refrigerant containing R1132(E); or a mixed refrigerant containing R1123.

[0066] The refrigeration cycle apparatus 200 according to this embodiment includes the compressor 100 according to this embodiment, an outdoor heat exchanger 104, a pressure reducer 105, and an indoor heat exchanger 106. With this configuration, the refrigeration cycle apparatus 200 can achieve the same effects as those described above.

[0067] Second Embodiment A compressor according to a second embodiment will now be described. Fig. 7 is a schematic cross-sectional view showing the configuration of a cylinder of a compressor according to this embodiment. Fig. 7 shows a cross section corresponding to Fig. 6.

[0068] In the first embodiment, the first surface 52, the second surface 53, the third surface 54, and the fourth surface 55 are all inclined with respect to the central axis L1. In contrast, in the present embodiment, as shown in Fig. 7, the second surface 53 and the fourth surface 55 are formed parallel to the central axis L1. The other configurations of the present embodiment are the same as those of the first embodiment. This embodiment can also achieve substantially the same effects as those of the first embodiment.

[0069] Third Embodiment A compressor according to a third embodiment will be described. Fig. 8 is a schematic top view showing the configuration of the cylinder of the compressor according to this embodiment. As shown in Fig. 8, the intersecting line L3 obliquely intersects with the radial line L2 in a plan view of the cylinder 23 seen along the axial direction. That is, the intersecting line L3 obliquely intersects with the radial line L2 in a cross section perpendicular to the central axis L1. Both the intersecting line L3 and the radial line L2 are included in the plane of the cross section perpendicular to the central axis L1.

[0070] The bridge portion 51-1 is formed to extend along the intersecting straight line L3. In other words, the bridge portion 51-1 is formed to extend obliquely with respect to the radial line L2 in a cross section perpendicular to the central axis L1 of the cylinder 23. The bridge portions 51-2 and 51-3 have the same configuration as the bridge portion 51-1. The other configurations are the same as those in the first embodiment.

[0071] The length a1 of the bridge portion 51-1 in the circumferential direction of the cylinder 23 is shorter than the length a2 of the arc hole 50 in the circumferential direction of the cylinder 23. Of the multiple bridge portions 51-1, 51-2, and 51-3, the two bridge portions 51-1 and 51-2 are arranged in positions facing each other across the central axis L1.

[0072] As described above, in the compressor 100 according to this embodiment, the intersecting line L3 intersects the radial line L2 obliquely in a cross section perpendicular to the central axis L1.

[0073] With this configuration, when the bridge portion 51-1 is distorted and deformed due to the thermal influence during thermal caulking or welding, the stress generated in the bridge portion 51-1 is resolved into a component in the radial direction of the cylinder 23 and a component in the circumferential direction of the cylinder 23. This reduces the stress in the radial direction. Therefore, with this configuration, it is possible to suppress distortion of the inner peripheral surface of the cylinder 23 that would reduce the roundness of the inner peripheral surface of the cylinder 23.

[0074] DESCRIPTION OF SYMBOLS 10 Sealed container, 11 Upper container, 12 Lower container, 20 Compression mechanism, 21 Rotating shaft, 21a Main shaft portion, 21b Eccentric shaft portion, 21c Sub-shaft portion, 22 Rolling piston, 23 Cylinder, 23a Cylinder chamber, 23b Back pressure chamber, 23c Vane groove, 23d First axial end face, 23e Second axial end face, 24 Upper bearing, 25 Lower bearing, 26 Vane, 27 Discharge muffler, 30 Electric motor, 31 Rotor, 32 Rotor core, 33 Magnet insertion hole, 34 Permanent magnet, 35 Air hole, 41 Stator, 50 Circular arc hole, 51-1, 51-2, 51-3 Bridge portion, 52 First surface, 52a End, 53 Second surface, 54 Third surface, 54a End, 55 Fourth surface, 100 Compressor, 101 suction muffler, 101a suction connecting pipe, 102 discharge pipe, 103 four-way switching valve, 104 outdoor heat exchanger, 105 pressure reducer, 106 indoor heat exchanger, 200 refrigeration cycle device, L1 central axis line, L2 radial line, L3 intersecting line.

Claims

1. A compression mechanism for compressing the refrigerant, A sealed container housing the compression mechanism, Equipped with, The compression mechanism is A hollow cylindrical cylinder having vane grooves is fixed to the inner circumferential surface of the sealed container by heat scribing or welding, A rolling piston that rotates eccentrically along the inner circumferential surface of the cylinder, The system includes vanes that reciprocate within the vane grooves and partition the space between the inner circumferential surface of the cylinder and the rolling piston, The cylinder has a plurality of arc-shaped holes that extend in an arc shape along the circumferential direction of the cylinder and penetrate the cylinder in the axial direction of the cylinder. The cylinder has a bridge portion formed between two arc holes that are adjacent to each other in the circumferential direction among the plurality of arc holes, If we define a straight line extending radially from the central axis of the cylinder toward the bridge portion as a radial line, and a straight line that intersects the radial line diagonally at the bridge portion as an intersecting line, The bridge section is a compressor formed to extend along the intersecting straight line.

2. The compressor according to claim 1, wherein in a cross section passing through the central axis and the bridge portion and parallel to the central axis, the intersecting line intersects the radial line diagonally.

3. The compressor according to claim 2, wherein in the cross-section, the length of the bridge portion in the direction perpendicular to the intersecting line is shorter than the length of the cylinder in the axial direction.

4. The cylinder has a first axial end face facing one direction in the axial direction and a second axial end face facing the other direction in the axial direction. If the side surface of the bridge portion on the first axial end face side is defined as the first surface, the surface connecting the outer end of the first surface and the first axial end face in the radial direction is defined as the second surface, the side surface of the bridge portion on the second axial end face side is defined as the third surface, and the surface connecting the inner end of the third surface and the second axial end face in the radial direction is defined as the fourth surface, The first and second surfaces are formed such that their distance from each other increases as they approach the first axial end face. The third and fourth surfaces are formed such that their distance from each other increases as they approach the second axial end face. The compressor according to claim 2 or 3, wherein the first surface, the second surface, the third surface, and the fourth surface are all inclined with respect to the central axis.

5. The compressor according to claim 1, wherein in a cross section perpendicular to the central axis, the intersecting line intersects the radial line diagonally.

6. The compressor according to any one of claims 1 to 3, wherein the length of the bridge portion in the circumferential direction is shorter than the length of the arc hole in the circumferential direction.

7. The aforementioned bridge section has a plurality of bridge sections, The compressor according to any one of claims 1 to 3, wherein two of the plurality of bridge sections are arranged opposite each other across the central axis.

8. The compressor according to any one of claims 1 to 3, wherein the refrigerant is a single refrigerant from among R1234yf, R1234ze, R32, and R290, a mixed refrigerant containing one or more of R1234yf, R1234ze, R32, and R290, a mixed refrigerant containing R1132(E), or a mixed refrigerant containing R1123.

9. A compressor according to any one of claims 1 to 3, Outdoor heat exchanger, pressure reducer and indoor heat exchanger, A refrigeration cycle device equipped with a refrigeration cycle system.