Rotary compressor and refrigeration cycle device

Abstract

This invention provides a rotary compressor and refrigeration cycle device capable of suppressing costs. The rotary compressor of embodiment 1 includes a cylinder, a shaft, a rolling piston, and blades. The front end of the blade on the cylinder chamber side is hinged to the rolling piston, dividing the cylinder chamber into an intake chamber on the intake port side and a compression chamber on the discharge port side. The direction of the central axis of the rolling piston is designated as a first direction. A groove having a first cylindrical surface extending along the first direction is formed on the outer periphery of the rolling piston. The blade has a blade body and a bushing. The bushing is mounted on the front end of the blade body on the cylinder chamber side and is received in the groove to form a hinged connection. The bushing has a second cylindrical surface that slides with the first cylindrical surface. The bushing is formed within a range from the central axis of the second cylindrical surface that is less than or equal to the radius of curvature of the second cylindrical surface.

Description

Technical Field

[0001] Embodiments of the present invention relate to a rotary compressor and a refrigeration cycle device. Background Technology

[0002] In a refrigeration cycle system, a rotary compressor is used to compress the refrigerant. A rotary compressor has a cylinder, a rolling piston, and vanes. The cylinder has a chamber. The vanes are housed in a slit within the cylinder. In a hinged vane type (vane and roller connection structure) rotary compressor, the leading edge of the vane on the chamber side is hinged to the rolling piston. Cost control is required for rotary compressors and refrigeration cycle systems.

[0003] Existing technical documents Patent documents Patent Document 1: Japanese Patent Application Publication No. 8-151988 Patent Document 2: Japanese Patent Application Publication No. 2023-5307 Patent Document 3: International Publication No. 2020 / 155923 Summary of the Invention The technical problem that the invention aims to solve The technical problem to be solved by the present invention is to provide a rotary compressor and refrigeration cycle device that can suppress costs.

[0004] Solution to the above technical problems The rotary compressor of embodiment 1 includes a cylinder, a shaft, a rolling piston, and vanes. The cylinder has a cylindrical chamber that compresses fluid drawn in from an intake port and discharges it from an outlet port. The shaft is coaxial with the chamber, and an eccentric portion is located inside the chamber, offset from the central axis of the chamber. The rolling piston is cylindrical, coaxial with the eccentric portion, and rotatable about the eccentric portion, abutting against the side of the chamber via an oil surface. The vanes are received in a slit in the cylinder, and their front end on the chamber side is hinged to the rolling piston, dividing the chamber into an intake chamber on the intake port side and a compression chamber on the outlet port side. The direction of the central axis of the rolling piston is designated as a first direction. A groove with a first cylindrical surface extending along the first direction is formed on the outer periphery of the rolling piston. The vanes have a vane body and a bushing. The bushing is mounted on the front end of the vane body on the chamber side and is received in the groove, forming a hinged connection. The bushing has a second cylindrical surface that slides against the first cylindrical surface. The bushing is formed within a range that is below the radius of curvature of the second cylindrical surface at a distance from the central axis of the second cylindrical surface.

[0005] Embodiment 2 is based on the rotary compressor described in Embodiment 1. In the mounting portion of the blade body and the bushing, the first surface of the blade body and the second surface of the bushing are arranged opposite each other. In at least a portion of the mounting portion in the first direction, the distance between the first surface and the second surface on the suction chamber side is greater than the distance between the first surface and the second surface on the compression chamber side.

[0006] Embodiment 3 is based on the rotary compressor described in Embodiment 2. A cylindrical first hole is formed on the first surface, and a cylindrical second hole is formed on the second surface. The rotary compressor has a cylindrical pin that is inserted across both the first and second holes.

[0007] Embodiment 4 is based on the rotary compressor described in Embodiment 3. The diameter of one of the first and second holes is larger than the diameter of the other, and also larger than the diameter of the pin.

[0008] Embodiment 5 is based on the rotary compressor described in Embodiment 4. The direction in which the blade body and bushing are arranged is designated as the second direction, the bushing side of the blade body is designated as the first side of the second direction, and the blade body side of the bushing is designated as the second side of the second direction. It includes a limiting member that restricts the separation of the blade body from the bushing towards the second side of the second direction. It does not include a force-applying member that applies force to the blade body toward the bushing along the first side of the second direction.

[0009] Embodiment 6 is based on the rotary compressor described in Embodiment 5. The limiting component allows relative movement between the blade body and the bushing in the first direction.

[0010] Embodiment 7 is based on the rotary compressor described in Embodiment 6. The limiting component is a screw. The head of the screw is received in a countersunk hole formed on the first side in the second direction of the bushing. The external thread formed on the body of the screw engages with the internal thread formed in the screw hole in the blade body. The front end face of the screw abuts against the bottom surface of the screw hole.

[0011] Embodiment 8 is based on the rotary compressor described in any one of embodiments 1 to 7. The direction in which the blade body and bushing are arranged is designated as the second direction, and the bushing side of the blade body is designated as the first side of the second direction. The rolling piston has a lubricating oil supply passage that extends radially and opens into a groove. The bushing has a bushing recess on the first side of the second direction, the distance from the central axis of the second cylindrical surface being smaller than the radius of curvature of the second cylindrical surface. The lubricating oil supply passage opens into the bushing recess.

[0012] Embodiment 9 is based on the rotary compressor described in any one of embodiments 1 to 8. The rolling piston is made of aluminum or an aluminum alloy.

[0013] The refrigeration cycle apparatus of the embodiment includes: a rotary compressor as described in any one of embodiments 1 to 8; a radiator connected to the rotary compressor; an expansion device connected to the radiator; and a heat absorber connected to the expansion device. Attached Figure Description

[0014] Figure 1 This is a circuit diagram of the refrigeration cycle device and a cross-sectional view of the rotary compressor in the embodiment.

[0015] Figure 2 yes Figure 1 A cross-sectional view of the compression mechanism section of line II-II.

[0016] Figure 3 yes Figure 2 Enlarged view of the periphery of the bushing.

[0017] Figure 4 yes Figure 2 Enlarged view of the bushing.

[0018] Figure 5 It is a three-dimensional exploded view of the leaf.

[0019] Figure 6 yes Figure 5 A sectional view along line VI-VI.

[0020] Figure 7 yes Figure 5 A sectional view along line VII-VII.

[0021] Figure 8 yes Figure 3 A cross-sectional view of line VIII-VIII.

[0022] Figure 9 yes Figure 8 Enlarged view of the surrounding area of ​​the sales.

[0023] Figure 10 yes Figure 8 A magnified view of the area around the screw. Detailed Implementation

[0024] Hereinafter, the rotary compressor and refrigeration cycle device of the embodiment will be described with reference to the accompanying drawings.

[0025] Figure 1 A circuit diagram of the refrigeration cycle device 1 in the embodiment is included. The refrigeration cycle device 1 has a rotary compressor 10, a four-way valve 3, a first heat exchanger 4, an expansion device 5, a second heat exchanger 6, and a refrigerant flow path 8 through which refrigerant (fluid) flows. The refrigerant circulates in the refrigeration cycle device 1 while undergoing a phase change.

[0026] The rotary compressor 10 compresses the low-pressure gaseous refrigerant drawn into it into a high-temperature, high-pressure gaseous refrigerant. A liquid receiver (gas-liquid separator) 2b is disposed upstream of the rotary compressor 10. The liquid receiver 2b separates the gaseous and liquid refrigerant, supplying the gaseous refrigerant to the rotary compressor 10.

[0027] The four-way valve 3 reverses the flow direction of the refrigerant in the refrigerant flow path 8 of the first heat exchanger 4, the expansion device 5, and the second heat exchanger 6. When the four-way valve 3 is in... Figure 1 In this state, the refrigerant discharged from the rotary compressor 10 flows in the order of the first heat exchanger 4, the expansion device 5, and the second heat exchanger 6. At this time, the first heat exchanger 4 functions as a condenser (radiator), and the second heat exchanger 6 functions as an evaporator (heat absorber).

[0028] When the four-way valve 3 is from Figure 1 When the state changes, the refrigerant discharged from the rotary compressor 10 flows in the order of the second heat exchanger 6, the expansion device 5, and the first heat exchanger 4. At this time, the second heat exchanger 6 functions as a condenser (radiator), and the first heat exchanger 4 functions as an evaporator (heat absorber).

[0029] The condenser dissipates heat from the high-temperature, high-pressure gaseous refrigerant discharged from the rotary compressor 10, transforming the high-temperature, high-pressure gaseous refrigerant into a high-pressure liquid refrigerant.

[0030] The expansion device 5 reduces the pressure of the high-pressure liquid refrigerant supplied from the condenser, transforming the high-pressure liquid refrigerant into a low-temperature, low-pressure gas-liquid two-phase refrigerant. For example, the expansion device 5 is an expansion valve.

[0031] The evaporator transforms the gas-liquid two-phase refrigerant fed from the expansion unit 5 into a low-pressure gaseous refrigerant. In the evaporator, the low-pressure gaseous two-phase refrigerant absorbs heat of vaporization from its surroundings during vaporization, thereby cooling the surroundings. The low-pressure gaseous refrigerant that has passed through the evaporator is drawn into the interior of the rotary compressor 10 via the receiver 2b.

[0032] Thus, in the refrigeration cycle unit 1, the refrigerant, serving as the working fluid, circulates while undergoing phase changes between gas and liquid. The refrigerant dissipates heat during its transition from gas to liquid and absorbs heat during its transition from liquid to gas. The refrigeration cycle unit 1 utilizes the heat dissipation or absorption of the refrigerant for heating, cooling, defrosting, and other functions.

[0033] Figure 1 This includes a cross-sectional view of the rotary compressor 10 in the embodiment. The cross-sectional view of the rotary compressor 10 is... Figure 2 A sectional view along line II. Figure 2 yes Figure 1 A cross-sectional view of the compression mechanism section 20 of line II-II.

[0034] In this application, the T, R, and θ directions of the cylindrical coordinate system are defined as follows: The T direction is the axial direction of the housing 11. The +T direction is the direction from the compression mechanism 20 toward the motor 14. For example, the T direction is the vertical direction, and the +T direction is vertically upward. The R direction is the radial direction of the housing 11. The +R direction is the direction outward from the radial direction. The θ direction is the circumferential direction of the housing 11. The +θ direction is the rotation direction of the right-hand screw moving in the +T direction. Furthermore, the opposite directions of the +T, +R, and +θ directions are respectively defined as the -T, -R, and -θ directions.

[0035] like Figure 1 As shown, the rotary compressor 10 has a housing 11, an electric motor 14, a shaft 15, a first bearing 30, a second bearing 35, a partition plate 33, a compression mechanism 20, a first silencer 38a, and a second silencer 38b.

[0036] The housing 11 is formed into a cylindrical shape closed at both ends. The housing 11 houses the motor section 14, the shaft 15, and the compression mechanism section 20. Lubricating oil 12, which lubricates the compression mechanism section 20, is contained inside the housing 11 in the -T direction. Gaseous refrigerant, compressed by the compression mechanism section 20, is contained inside the housing 11 in the +T direction. The gaseous refrigerant and lubricating oil inside the housing 11 are at high pressure. The gaseous refrigerant is supplied from the discharge port 13 in the +T direction of the housing 11 to the four-way valve 3 through the refrigerant flow path 8.

[0037] The motor unit 14 is disposed inside the housing 11 in the +T direction. The motor unit 14 has a stator 14a and a rotor 14b. The stator 14a is fixed to the inner circumferential surface of the housing 11. The rotor 14b is disposed in the -R direction of the stator 14a.

[0038] The shaft 15 and the housing 11 are configured coaxially. The rotor 14b of the motor unit 14 is fixed in the +T direction of the shaft 15. The shaft 15 has an eccentric portion 16 in the -T direction. The eccentric portion 16 is formed in a cylindrical shape. The eccentric portion 16 is eccentric from the central axis of the housing 11.

[0039] The first bearing (main bearing) 30 is disposed in the +T direction of the compression mechanism section 20. The first bearing 30 has a bearing section 31 and a closing section 32. The bearing section 31 of the first bearing 30 supports the shaft 15 in the +T direction of the compression mechanism section 20 so that it can rotate. The closing section 32 of the first bearing 30 closes the opening in the +T direction of the compression mechanism section 20.

[0040] The second bearing (sub-bearing) 35 is disposed in the -T direction of the compression mechanism section 20. The second bearing 35 has a bearing section 36 and a closing section 37. The bearing section 36 of the second bearing 35 supports the shaft 15 in the -T direction of the compression mechanism section 20 so that it can rotate. The closing section 37 of the second bearing 35 closes the opening in the -T direction of the compression mechanism section 20.

[0041] The compression mechanism 20 is disposed inside the housing 11 in the -T direction. The compression mechanism 20 can be a single-cylinder compression mechanism with one cylinder chamber 22, or a multi-cylinder compression mechanism with multiple cylinder chambers 22. Figure 1 In the example, the compression mechanism 20 has two cylinder chambers 22 arranged along the T direction.

[0042] The partition plate 33 is positioned between the two cylinder chambers 22.

[0043] The compression mechanism 20 includes a cylinder 21, a rolling piston 40, and a vane (sliding vane) 50 in each cylinder body (see reference). Figure 2 ).

[0044] The cylinder 21 and the housing 11 are configured coaxially. The cylinder 21 is fixed to the inner circumferential surface of the housing 11. Figure 2 As shown, cylinder 21 has a cylinder chamber 22. The cylinder chamber 22 is formed inside a through hole that extends through cylinder 21 along the T direction. The cylinder chamber 22 and housing 11 are coaxially formed. An eccentric portion 16 of shaft 15 is disposed inside the cylinder chamber 22.

[0045] The rolling piston 40 is cylindrical. The rolling piston 40 and the eccentric portion 16 are coaxially arranged. The rolling piston 40 is rotatable around the eccentric portion 16. A portion of the outer peripheral surface of the rolling piston 40 abuts against the inner peripheral surface of the cylinder 21 (the side surface of the cylinder chamber 22) via an oil film (oil surface) of several μm to tens of μm. The area between the outer peripheral surface of the rolling piston 40 and the inner peripheral surface of the cylinder 21 functions as a de facto cylinder chamber 22.

[0046] The cylinder 21 has a refrigerant intake port 25 and a refrigerant discharge port 26.

[0047] The intake port 25 extends along the R direction through the housing 11 and the cylinder 21. The intake port 25 will... Figure 1 The gaseous refrigerant supplied by the liquid receiver 2b is introduced into the interior of the cylinder chamber 22.

[0048] The discharge port 26 extends through the closed portion 32 of the first bearing 30 or the closed portion 37 of the second bearing 35 in the T direction. A reed valve is disposed on the opposite side of the cylinder chamber 22, separated by the discharge port 26. The reed valve opens and closes the discharge port 26 according to the pressure in the cylinder chamber 22. The discharge port 26 discharges the compressed gaseous refrigerant in the cylinder chamber 22 to the outside of the cylinder chamber 22.

[0049] like Figure 2As shown, the blade 50 is accommodated in a slit 27 formed in the cylinder 21. The slit 27 extends through the cylinder 21 in the T direction. The slit 27 extends, for example, in the R direction. The -R direction end of the slit 27 opens into the cylinder chamber 22. A back pressure chamber 28 is formed at the +R direction end of the slit. High-pressure lubricating oil 12 (see reference) Figure 1 It enters the back pressure chamber 28. The pressure of the lubricating oil 12 in the back pressure chamber 28 presses the blade 50 in the -R direction.

[0050] The leading edge of blade 50 in the -R direction is hinged to rolling piston 40. As shaft 15 rotates, eccentric portion 16 and rolling piston 40 revolve in the θ direction inside cylinder chamber 22 (eccentric rotation). Accompanying the revolution of rolling piston 40, blade 50 advances and retracts in the R direction. Blade 50 divides the interior of cylinder chamber 22 into suction chamber 23 on the suction port 25 side and compression chamber 24 on the discharge port 26 side.

[0051] like Figure 1 As shown, the first silencer 38a is disposed in the +T direction of the closed portion 32 of the first bearing 30. A first silencing chamber is formed between the first silencer 38a and the first bearing 30. The first silencing chamber contains high-pressure gaseous refrigerant discharged from the discharge port 26 of the first bearing 30.

[0052] The second silencer 38b is disposed in the -T direction of the enclosure 37 of the second bearing 35. A second silencing chamber is formed between the second silencer 38b and the second bearing 35. The second silencing chamber contains high-pressure gaseous refrigerant discharged from the discharge port 26 of the second bearing 35.

[0053] The gaseous refrigerant in the second silencer chamber moves into the first silencer chamber through a through hole (not shown) that passes through the cylinder 21 in the T direction. The gaseous refrigerant in the first silencer chamber is discharged into the interior of the housing 11 through the opening of the first silencer 38a.

[0054] The blade 50 is described in detail.

[0055] Figure 3 yes Figure 2 An enlarged view of the periphery of the bushing 60. A groove 42 is formed on the outer periphery of the rolling piston 40. The groove 42 extends through the rolling piston 40 along the T direction. The inner surface of the groove 42 is a first cylindrical surface 42c extending along the T direction. The opening width of the groove 42 is smaller than the diameter of the bushing 60 described below.

[0056] like Figure 2 As shown, the blade 50 has a blade body 51 and a bushing 60.

[0057] The blade body 51 is formed into a flat plate shape from metal materials such as iron, aluminum, or aluminum alloy. Alternatively, other resins, ceramics, or composite materials containing these materials can also be used. The blade body 51 is housed in the slit 27 of the cylinder 21. Figure 3 As shown, a bushing 60 is installed on the first surface 51s at the front end of the blade body 51 in the -R direction.

[0058] In this application, the Z, X, and Y directions of the orthogonal coordinate system, which serves as the local coordinate system for the blade 50, are defined as follows: The Z direction is the height direction of the blade body 51. For example, the Z direction corresponds to the T direction, and the +Z direction corresponds to the +T direction. The Z direction (first direction) is also the direction of the central axis of the rolling piston 40. The X direction is the length direction of the blade body 51. For example, the X direction corresponds to the R direction, and the +X direction corresponds to the -R direction. The X direction (second direction) is also the direction in which the blade body 51 and the bushing 60 are arranged. The +X direction (first side of the second direction) is the bushing 60 side of the blade body 51. The -X direction (second side of the second direction) is the blade body 51 side of the bushing 60. The Y direction is the width direction of the blade body 51. For example, the Y direction corresponds to the tangent direction of the θ direction. Furthermore, the opposite directions of the +Z, +X, and +Y directions are defined as the -Z, -X, and -Y directions, respectively.

[0059] Figure 4 yes Figure 2 Enlarged view of bushing 60.

[0060] The bushing 60 is made of metal materials such as high-speed tool steel. High-speed tool steel is easy to machine and has excellent wear resistance. For example... Figure 4 As shown, the bushing 60 has a second cylindrical surface 60c. The second cylindrical surface 60c intersects with the first cylindrical surface 42c of the groove 42 of the rolling piston 40 (see reference). Figure 3 Sliding. Bushing 60 has a second surface 60s in the -X direction. (e.g.) Figure 6 As shown, in the mounting portion 50m between the blade body 51 and the bushing 60, the first surface 51s of the blade body 51 and the second surface 60s of the bushing 60 are arranged opposite each other. For example, the second surface 60s is a plane. Figure 4 As shown, the bushing 60 has a bushing recess 64 in the +X direction. The bushing recess 64 is recessed further toward the central axis 61 than the imaginary surface formed by extending the second cylindrical surface 60c. For example, the bottom surface 63 of the bushing recess 64 is a plane.

[0061] The bushing 60 is formed within a range from the central axis 61 of the second cylindrical surface 60c to a radius of curvature 62 or less of the second cylindrical surface 60c. The bushing 60 does not have any portion whose distance from the central axis 61 exceeds the radius of curvature 62. Therefore, the bushing 60 can be manufactured as follows: First, a cylindrical intermediate part is formed by machining and grinding the base material while rotating it using a lathe or the like. The outer periphery of the intermediate part corresponds to the second cylindrical surface 60c. Next, the intermediate part is machined using a milling machine or the like, thereby forming the second surface 60s in the -X direction and the bottom surface 63 of the bushing recess 64 in the +X direction. Since the bushing 60 can be manufactured in this way, the manufacturing cost of the bushing 60 can be reduced. Furthermore, the accuracy of the dimensions, surface roughness, and cylindricality of the second cylindrical surface 60c is improved.

[0062] Figure 5 This is an exploded perspective view of the blade 50. As described above, the blade 50 divides the cylinder chamber 22 into an intake chamber 23 and a compression chamber 24. The blade body 51 has a recess 52 on its side surface from the first surface 51s in the +X direction to the intake chamber 23 side. The recess 52 opens towards the intake chamber 23 side of the blade body 51 but does not open towards the compression chamber 24 side. The two recesses 52 are formed separately in the +Z and -Z directions of the first surface 51s. No recesses are formed at the end of the compression chamber 24 side in the Y direction of the first surface 51s, or at the central portion and both ends in the Z direction. The non-formed area of ​​the recess 52 in the first surface 51s is a plane. That is, a plane extending along the entire Z direction is formed at the end of the compression chamber 24 side of the first surface 51s. The recess 52 may also be formed continuously along the entire Z direction on the intake chamber 23 side of the first surface 51s.

[0063] Figure 6 yes Figure 5 A cross-sectional view along line VI-VI (the non-forming area of ​​recess 52). As described above, the second surface 60s of the bushing 60 in the -X direction is a plane. The first surface 51s of the blade body 51 in the +X direction is a plane in the non-forming area of ​​recess 52. In the non-forming area of ​​recess 52, the first surface 51s of the blade body 51 is in contact with the second surface 60s of the bushing 60. The distance between the first surface 51s and the second surface 60s on the suction chamber 23 side and the distance between the first surface 51s and the second surface 60s on the compression chamber 24 side are both zero.

[0064] Figure 7 yes Figure 5A cross-sectional view along line VII-VII (the region where the recess 52 is formed). As described above, the recess 52 opens toward the intake chamber 23 side of the blade body 51 but not toward the compression chamber 24 side. The distance between the first surface 51s and the second surface 60s on the compression chamber 24 side is zero. In the region where the recess 52 is formed, the first surface 51s of the blade body 51 is separated from the second surface 60s of the bushing 60. The distance G between the first surface 51s and the second surface 60s on the intake chamber 23 side is greater than the distance between the first surface 51s and the second surface 60s on the compression chamber 24 side.

[0065] In this way, in at least a portion of the mounting section 50m along the Z direction, the interval between the first surface 51s and the second surface 60s on the suction chamber 23 side is greater than the interval between the first surface 51s and the second surface 60s on the compression chamber 24 side. The low pressure of the gaseous refrigerant in the suction chamber 23 acts on the first surface 51s in the +X direction of the blade body 51. Figure 2 As shown, the high pressure of the lubricating oil in the back pressure chamber 28 acts on the end face of the blade body 51 in the -X direction. This presses the blade body 51 against the bushing 60 in the +X direction, suppressing separation of the blade body 51 from the bushing 60 (blade slippage). This also suppresses abnormal noise caused by the re-aperture between the blade body 51 and the bushing 60. Furthermore, it suppresses leakage of gaseous refrigerant from the compression chamber 24 to the suction chamber 23.

[0066] In one embodiment, a recess 52 opening toward the suction chamber 23 is formed on the first surface 51s of the blade body 51. Conversely, a recess opening toward the suction chamber 23 may also be formed on the second surface 60s of the bushing 60. Furthermore, recesses opening toward the suction chamber 23 may be formed on both the first surface 51s and the second surface 60s. Even in these cases, in at least a portion of the Z-direction of the mounting portion 50m, the distance between the first surface 51s and the second surface 60s on the suction chamber 23 side is greater than the distance between the first surface 51s and the second surface 60s on the compression chamber 24 side.

[0067] In this embodiment, both the non-formed area of ​​the recess 52 in the first surface 51s of the blade body 51 and the second surface 60s of the bushing 60 are planar. Conversely, the first surface 51s and the second surface 60s in the non-formed area of ​​the recess 52 can also be curved surfaces of the same shape. Thus, in the non-formed area of ​​the recess, the first surface 51s and the second surface 60s are arranged opposite each other and in surface contact.

[0068] like Figure 5 As shown, blade 50 has screw 70 and a pair of pins 78.

[0069] Figure 8 yes Figure 3A sectional view along line VIII-VIII. Screw 70 is positioned at the center of the mounting portion 50m in the Z direction. A pair of pins 78 are separately positioned in the +Z and -Z directions of the mounting portion 50m. The central axis of screw 70 and the pair of pins 78 is along the X direction.

[0070] Figure 9 yes Figure 8 An enlarged view of the periphery of pin 78. Pin 78 is cylindrical. Pin 78 can be a solid rod or a spring pin. A first hole 58 is formed on the first surface 51s of the blade body 51. A second hole 68 is formed on the second surface 60s of the bushing 60. Both the first hole 58 and the second hole 68 are cylindrical. The central axis of the first hole 58 and the second hole 68 is along the X direction. Pin 78 is inserted across both the first hole 58 and the second hole 68. This suppresses the offset of the blade body 51 and the bushing 60 in the Y direction.

[0071] The diameter of one of the holes, 58 (first hole) and 68 (second hole), is larger than the diameter of the other, and also larger than the diameter of pin 78. Figure 9 In this example, the diameter of the first hole 58 is larger than the diameter of the second hole 68, and also larger than the diameter of the pin 78. The diameter of the second hole 68 is smaller than the diameter of the pin 78. The pin 78 is pressed into the second hole 68. This prevents the pin 78 from falling out. Furthermore, the pin 78 is not pressed into the first hole 58. This facilitates the assembly of the blade body 51 and the bushing 60. Additionally, there is a gap between the end of the pin 78 in the -X direction and the bottom of the first hole 58.

[0072] Pin 78 is pressed into the second hole 68 of bushing 60, but not into the first hole 58 of blade body 51. The size of bushing 60 in the X direction is smaller than that of blade body 51. Pressing pin 78 into the second hole 68 of bushing 60 in the X direction is easier than pressing pin into the first hole 58 of blade body 51.

[0073] Figure 10 yes Figure 8 An enlarged view of the periphery of screw 70. Screw 70 is a limiting component that restricts the separation of blade body 51 from bushing 60 in the -X direction. A rivet or similar component may also be used instead of screw 70 as the limiting component. Screw 70 has a head 71 and a body 72. The head 71 is located at the end in the +X direction, and the body 72 is located in the -X direction of the head 71. An external thread 73 is formed in the middle portion of the body 72 in the X direction.

[0074] As described above, a bushing recess 64 is formed in the +X direction of the bushing 60. A countersunk hole 65 is formed on the bottom surface 63 of the bushing recess 64. The head 71 of the screw 70 is accommodated inside the countersunk hole 65. The diameter of the countersunk hole 65 is larger than the diameter of the head 71. A gap exists between the bottom surface of the countersunk hole 65 and the head 71. A through hole is formed from the bottom surface of the countersunk hole 65 to the second surface 60s of the bushing 60. The diameter of this through hole is smaller than the diameter of the head 71 and larger than the diameter of the body 72.

[0075] A cylindrical screw hole 55 is formed on the first surface 51s of the blade body 51. An internal thread 53 is formed in the region of the screw hole 55 in the +X direction. The external thread 73 of the screw 70 engages (screws) with the internal thread 53 of the screw hole 55. Thus, the screw 70 restricts the blade body 51 from separating from the bushing 60 in the -X direction. Figure 2 The compressor unit 20 shown does not have a force-applying component that applies force to the blade body 51 toward the bushing 60 in the +X direction. In this case, it is also possible to prevent the blade body 51 from separating from the bushing 60 in the -X direction. Since there is no force-applying component, the inner diameter of the cylinder 21 can be increased. As a result, the height of the cylinder 21 can be reduced, and the rotary compressor 10 can be miniaturized.

[0076] The internal thread 53 is formed only in the +X direction region of the screw hole 55. No internal thread 53 is formed in the -X direction region of the screw hole 55. The diameter of the screw hole 55 is larger than the diameter of the body 72 of the screw 70. Both the bottom surface 56 of the screw hole 55 and the front end face 76 of the screw 70 are flat. The front end face 76 of the screw 70 abuts against the bottom surface 56 of the screw hole 55. Thus, the screw 70 is precisely positioned in the specified position in the X direction. A small gap is ensured between the head 71 of the screw 70 and the bottom surface of the countersunk hole 65. By minimizing the size of this gap, the separation of the blade body 51 from the bushing 60 can be minimized.

[0077] like Figure 9 As shown, the diameter of the first hole 58 of the blade body 51 is larger than the diameter of the pin 78 pressed into the bushing 60. The blade body 51 and the bushing 60 are able to move relative to each other in the Z direction within the limits of the gap between the first hole 58 and the pin 78. The screw 70 allows the relative movement of the blade body 51 and the bushing 60 in the Z direction.

[0078] The height of the blade body 51 and bushing 60 in the Z direction is slightly less than the height of the cylinder 21 in the Z direction. Therefore, the blade body 51 and bushing 60 can move inside the cylinder chamber 22. Assuming the blade body 51 and bushing 60 are rigidly joined by screws 70, the bushing 60 may be fixed in a state where it protrudes from the blade body 51 in the Z direction. In this case, with the blade body 51 and bushing 60 rigidly joined, it is necessary to machine the protruding portion of the bushing 60.

[0079] In contrast, the blade body 51 and bushing 60 of the embodiment are capable of relative movement in the Z direction. The blade body 51 and bushing 60 are not fixed in a state of offset in the Z direction. With the blade body 51 and bushing 60 rigidly engaged, there is no need for machining to remove the protrusion of the bushing 60. Therefore, the manufacturing cost of the rotary compressor is reduced.

[0080] like Figure 3 As shown, the bushing 60 is accommodated in the groove 42 of the rolling piston 40. The first cylindrical surface 42c of the groove 42 and the second cylindrical surface 60c of the bushing 60 are arranged coaxially and slide relative to each other. Thus, the +X direction end of the blade 50 is hinged to the rolling piston 40.

[0081] As mentioned above, in Figure 1 The lower part of the housing 11 shown contains lubricating oil 12. A first oil supply passage 17 is formed inside the shaft 15 along its central axis. A pump unit (not shown), such as a torsion plate, is installed inside the first oil supply passage 17. The pump unit draws lubricating oil 12 from the lower part of the housing 11 upwards as the shaft 15 rotates. A second oil supply passage 18 is formed radially through the shaft 15 from the first oil supply passage 17 to the outer periphery of the shaft 15. The lubricating oil 12 is supplied through the second oil supply passage 18 to the eccentric part 16 and the sliding part of the rolling piston 40, etc.

[0082] like Figure 3 As shown, the rolling piston 40 has a lubricating oil supply passage 44. The lubricating oil supply passage 44 extends radially through the rolling piston 40 and opens into the groove 42. As described above, the bushing 60 has a bushing recess 64 in the +X direction. The lubricating oil supply passage 44 opens into the bushing recess 64. Lubricating oil 12 is stored in the bushing recess 64 through the lubricating oil supply passage 44. The lubricating oil 12 is supplied from the bushing recess 64 to the sliding portion between the groove 42 and the bushing 60. Thus, the hinge engagement between the rolling piston 40 and the blade 50 operates smoothly.

[0083] Along with this, the rolling piston 40 can be formed from materials such as aluminum or aluminum alloy. Furthermore, the blade body 51 can be formed from materials such as aluminum or aluminum alloy. As a result, the rotary compressor 10 can be made lighter. In addition, vibrations associated with the eccentric rotation of the eccentric portion 16 and the rolling piston 40 are suppressed. The weight of the balancer installed on the shaft 15 to reduce vibration can be reduced.

[0084] As detailed above, the rotary compressor 10 of this embodiment includes a cylinder 21, a shaft 15, a rolling piston 40, and vanes 50. The cylinder 21 has a cylindrical chamber 22 that compresses fluid drawn in from a suction port 25 and discharges it from a discharge port 26. The shaft 15 is coaxial with the chamber 22, and the interior of the chamber 22 has an eccentric portion 16 eccentric to the central axis of the chamber 22. The rolling piston 40 is cylindrical, coaxial with the eccentric portion 16, and is rotatable about the eccentric portion 16, abutting against the side of the chamber 22 via an oil film. The vanes 50 are housed in a slit 27 of the cylinder 21, and the front end of the chamber 22 is hinged to the rolling piston 40, dividing the chamber 22 into a suction chamber 23 on the suction port 25 side and a compression chamber 24 on the discharge port 26 side. The direction of the central axis of the rolling piston 40 is defined as the Z-direction. A groove 42 with a first cylindrical surface 42c extending in the Z direction is formed on the outer periphery of the rolling piston 40. The blade 50 has a blade body 51 and a bushing 60. The bushing 60 is mounted on the front end of the blade body 51 on the cylinder chamber 22 side and is received in the groove 42 to form a hinged connection. The bushing 60 has a second cylindrical surface 60c that slides with the first cylindrical surface 42c. The bushing 60 is formed within a range from the central axis of the second cylindrical surface 60c that is less than or equal to the radius of curvature 62 of the second cylindrical surface 60c.

[0085] According to this configuration, the second cylindrical surface 60c of the bushing 60 can be formed by machining while rotating the base material. Therefore, the cost of the rotary compressor 10 can be reduced.

[0086] In the mounting portion 50m of the blade body 51 and the bushing 60, the first surface 51s of the blade body 51 and the second surface 60s of the bushing 60 are arranged opposite each other. In at least a portion of the mounting portion 50m in the Z direction, the distance G between the first surface 51s and the second surface 60s on the suction chamber 23 side is greater than the distance between the first surface 51s and the second surface 60s on the compression chamber 24 side.

[0087] According to this configuration, the low pressure of the gaseous refrigerant in the suction chamber 23 acts on the first surface 51s in the +X direction of the blade body 51. On the other hand, the high pressure of the lubricating oil in the back pressure chamber 28 acts on the end face of the blade body 51 in the -X direction. As a result, the blade body 51 is pressed towards the bushing 60 in the +X direction. Separation between the blade body 51 and the bushing 60 can be suppressed.

[0088] A cylindrical first hole 58 is formed on the first surface 51s, and a cylindrical second hole 68 is formed on the second surface 60s. The rotary compressor 10 has a cylindrical pin 78 that is inserted across both the first hole 58 and the second hole 68.

[0089] This can suppress the offset of the blade body 51 and the bushing 60 in the Y direction.

[0090] The diameter of one of the holes, 58 (first hole) and 68 (second hole), is larger than the diameter of the other hole, and is also larger than the diameter of the pin 78.

[0091] This prevents the pin 78 from falling off. Furthermore, the assembly of the blade body 51 and the bushing 60 is easy.

[0092] The direction in which the blade body 51 and the bushing 60 are arranged is designated as the X direction, the bushing 60 side of the blade body 51 is designated as the +X direction, and the blade body 51 side of the bushing 60 is designated as the -X direction. A screw 70 is provided to restrict the separation of the blade body 51 from the bushing 60 in the -X direction. No force-applying component is provided to apply force to the blade body 51 toward the bushing 60 in the +X direction.

[0093] Since it lacks a force-applying component, the inner diameter of cylinder 21 can be increased. As a result, the height of cylinder 21 can be reduced, and the rotary compressor 10 can be miniaturized.

[0094] Screw 70 allows relative movement of the blade body 51 and bushing 60 in the Z direction.

[0095] Therefore, the blade body 51 and bushing 60 are not fixed in a state of offset in the Z direction. There is no need for machining the portion of the bushing 60 protruding from the blade body 51. Thus, the manufacturing cost of the rotary compressor can be reduced.

[0096] The head 71 of the screw 70 is received in a countersunk hole 65 formed in the +X direction of the bushing 60. The external thread 73 formed in the body 72 of the screw 70 engages with the internal thread 53 formed in the screw hole 55 of the blade body 51. The front end face 76 of the screw 70 abuts against the bottom surface 56 of the screw hole 55.

[0097] Therefore, the screw 70 is precisely positioned at a predetermined location in the X direction. A minute gap is ensured between the head 71 of the screw 70 and the bottom surface of the countersunk hole 65. By minimizing the size of the gap, the separation of the blade body 51 from the bushing 60 can be minimized.

[0098] The direction in which the blade body 51 and the bushing 60 are arranged is designated as the X direction, and the bushing 60 side of the blade body 51 is designated as the +X direction. The rolling piston 40 has a lubricating oil supply passage 44 that extends radially and opens into a groove 42. The bushing 60 has a bushing recess 64 in the +X direction, the distance from the central axis of the second cylindrical surface 60c being smaller than the radius of curvature 62 of the second cylindrical surface 60c. The lubricating oil supply passage 44 opens into the bushing recess 64.

[0099] Lubricating oil 12 is stored in bushing recess 64 through lubricating oil supply passage 44. Lubricating oil 12 is supplied from bushing recess 64 to the sliding portion between groove 42 and bushing 60. As a result, the hinge engagement between rolling piston 40 and blade 50 operates smoothly.

[0100] Furthermore, the lubricating oil supply passage 44 formed on the rolling piston 40 can be a groove formed on the axial end face of the rolling piston 40 instead of a through hole. In particular, by making the lubricating oil supply passage 44 a groove formed on the axial end face of the rolling piston 40, or a through hole formed near the axial end face, the second oil supply passage 18, the axial end face of the eccentric portion 16, and the lubricating oil supply passage 44 can be kept in a state of constant communication. As a result, without performing unnecessary machining on the eccentric portion 16, refrigeration oil can be continuously supplied to the bushing 60 side when the rotary compressor 10 is running.

[0101] The rolling piston 40 is made of aluminum or an aluminum alloy.

[0102] As a result, the rotary compressor 10 can be made lighter.

[0103] The refrigeration cycle apparatus 1 of the embodiment includes: the aforementioned rotary compressor 10, one of the first heat exchanger 4 and the second heat exchanger 6 functioning as radiators, an expansion device 5, and the other of the first heat exchanger 4 and the second heat exchanger 6 functioning as absorbers. The radiator is connected to the rotary compressor 10. The expansion device 5 is connected to the radiator. The absorber is connected to the expansion device 5.

[0104] By having the rotary compressor 10 described above, the cost of the refrigeration cycle unit 1 can be reduced.

[0105] According to at least one embodiment described above, a bushing 60 is formed at a distance from the central axis of the second cylindrical surface 60c within a range below the radius of curvature 62 of the second cylindrical surface 60c. This allows for cost reduction of the rotary compressor 10.

[0106] Several embodiments of the present invention have been described, but these embodiments are provided by way of example and are not intended to limit the scope of the invention. These embodiments can be implemented in various other ways, and various omissions, substitutions, and modifications can be made without departing from the spirit of the invention. These embodiments and their variations are included in the scope and spirit of the invention, and are included in the scope of the invention as set forth in the claims and its equivalents.

[0107] Explanation of reference numerals in the attached figures G interval 1. Refrigeration circulation unit 4. First heat exchanger (radiator, absorber) 5. Expansion device 6. Second heat exchanger (absorber, radiator) 10 Rotary compressor 15-axis 16. Eccentric part 21 cylinders 22 cylinder chambers 23 Inhalation Chamber 24 Compression Chamber 25 Suction port 26 Discharge port 27. Slit 40 Rolling Piston 42. Groove 42c First cylindrical surface 44 Lubricating oil supply path 50 blades 50m Installation Section 51. Blade body 51s, Page 1 53 Internal thread 55 screw hole 56 Bottom 58 Hole 1 60 bushing 60s, Page 2 61 Central axis 62 Radius of curvature 64 Bushing Recess 65 countersunk holes 70 Screws (Restricting Parts) 71 Head 72. Torso 73 External thread 76 Front end 78 sold.

Claims

1. A rotary compressor, characterized in that, have: A cylinder having a cylindrical chamber that compresses fluid drawn in from an intake port and discharges it from an exhaust port; The shaft is configured coaxially with the cylinder chamber and has an eccentric portion inside the cylinder chamber that is off-center from the central axis of the cylinder chamber; A rolling piston, formed in a cylindrical shape, is coaxially arranged with the eccentric portion, and can rotate around the eccentric portion, and can abut against the side of the cylinder chamber via the oil surface; The blades, housed in the slits of the cylinder, have their front ends on the cylinder chamber side hinged to the rolling piston, dividing the cylinder chamber into an intake chamber on the intake port side and a compression chamber on the exhaust port side. When the direction of the central axis of the rolling piston is set as the first direction, a groove having a first cylindrical surface extending along the first direction is formed on the outer periphery of the rolling piston. The blade has: a blade body; and a bushing, which is installed at the front end of the blade body on the cylinder chamber side and is received in the groove to form the hinge connection. The bushing has a second cylindrical surface that slides with the first cylindrical surface. The bushing is formed within a range that is below the radius of curvature of the second cylindrical surface at a distance from the central axis of the second cylindrical surface.

2. The rotary compressor as described in claim 1, characterized in that, In the mounting portion between the blade body and the bushing, the first surface of the blade body and the second surface of the bushing are arranged opposite each other. In at least a portion of the first direction of the mounting portion, the distance between the first surface and the second surface on the suction chamber side is greater than the distance between the first surface and the second surface on the compression chamber side.

3. The rotary compressor as described in claim 2, characterized in that, A cylindrical first hole is formed on the first surface, and a cylindrical second hole is formed on the second surface. The rotary compressor has a cylindrical pin that is inserted across both the first hole and the second hole.

4. The rotary compressor as described in claim 3, characterized in that, The diameter of one of the first hole and the second hole is larger than the diameter of the other hole, and is also larger than the diameter of the pin.

5. The rotary compressor as described in claim 4, characterized in that, When the direction in which the blade body and the bushing are arranged is designated as the second direction, the bushing side of the blade body is designated as the first side of the second direction, and the blade body side of the bushing is designated as the second side of the second direction, It has a limiting member that restricts the separation of the blade body from the bushing to the second side in the second direction. It does not have a force-applying component that applies force to the blade body toward the bushing along the first side of the second direction.

6. The rotary compressor as described in claim 5, characterized in that, The limiting component allows relative movement of the blade body and the bushing in the first direction.

7. The rotary compressor as described in claim 6, characterized in that, The limiting component is a screw. The head of the screw is received in a countersink formed on the first side of the bushing in the second direction. The external thread formed on the body of the screw engages with the internal thread formed in the screw hole on the blade body. The front end face of the screw abuts against the bottom surface of the screw hole.

8. The rotary compressor as described in claim 1, characterized in that, When the direction in which the blade body and the bushing are arranged is designated as the second direction, and the bushing side of the blade body is designated as the first side of the second direction, The rolling piston has a lubricating oil supply path that extends radially through and opens into the groove. The bushing has a bushing recess on the first side in the second direction, the distance from the central axis of the second cylindrical surface being smaller than the radius of curvature of the second cylindrical surface. The lubricating oil supply path is directed toward the bushing recess opening.

9. The rotary compressor as described in claim 1 or 8, characterized in that, The rolling piston is made of aluminum or an aluminum alloy.

10. A refrigeration cycle device, characterized in that, have: The rotary compressor as described in claim 1 or 2; A radiator is connected to the rotary compressor; An expansion device is connected to the radiator; A heat absorber is connected to the expansion device.

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