Rotary compressors and refrigeration cycle systems
The rotary compressor's vane and bush design addresses cost suppression and operational efficiency by minimizing vane separation and refrigerant leakage, resulting in a compact and cost-effective rotary compressor.
Patent Information
- Authority / Receiving Office
- JP · JP
- Patent Type
- Applications
- Current Assignee / Owner
- CARRIER JAPAN CORP
- Filing Date
- 2024-12-18
- Publication Date
- 2026-06-30
AI Technical Summary
There is a demand to suppress costs in rotary compressors and refrigeration cycle apparatuses, particularly in the design of vane-roller connection structures within rotary compressors.
The rotary compressor incorporates a vane and bush design where the bush is formed with a second cylindrical surface that slides against a first cylindrical surface, with specific alignment and distance configurations to minimize manufacturing costs and prevent vane separation, while allowing for a compact design and efficient operation.
This design reduces manufacturing costs, suppresses vane separation and refrigerant leakage, and enables a more compact rotary compressor with improved operational efficiency.
Smart Images
Figure 2026106622000001_ABST
Abstract
Description
Technical Field
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[0001] Embodiments of the present invention relate to a rotary compressor and a refrigeration cycle apparatus.
Background Art
[0002] In a refrigeration cycle apparatus, a rotary compressor is used to compress a refrigerant. The rotary compressor has a cylinder, a roller piston, and a vane. The cylinder has a cylinder chamber. The vane is housed in a slit of the cylinder. In a hinged vane type (vane-roller connection structure) rotary compressor, the tip of the vane on the cylinder chamber side is hinged to the roller piston. There is a demand to suppress costs in the rotary compressor and the refrigeration cycle apparatus.
Prior Art Documents
Patent Documents
[0003]
Patent Document 1
Patent Document 2
Patent Document 3
Summary of the Invention
Problems to be Solved by the Invention
[0006] Embodiment 2 is based on the rotary compressor described in Embodiment 1. At the mounting portion between the vane body and the bush, the first surface of the vane body and the second surface of the bush are arranged facing 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.
[0007] 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 inserted across both the first and second holes.
[0008] Embodiment 4 is based on the rotary compressor described in Embodiment 3. The diameter of one of the first hole and the second hole is larger than the diameter of the other, and is also larger than the diameter of the pin.
[0009] Embodiment 5 is based on the rotary compressor described in Embodiment 4. The direction in which the vane body and the bush are aligned is defined as the second direction, the bush side of the vane body is defined as the first side in the second direction, and the vane body side of the bush is defined as the second side in the second direction. It has a regulating member that restricts the vane body from moving away from the bush to the second side in the second direction. It does not have a biasing member that biases the vane body toward the bush to the first side in the second direction.
[0010] Embodiment 6 is based on the rotary compressor described in Embodiment 5. The regulating member allows relative movement between the vane body and the bush in the first direction.
[0011] Embodiment 7 is based on the rotary compressor described in Embodiment 6. The regulating member is a screw. The head of the screw is housed in a counterbore formed on the first side in the second direction of the bush. The male threads formed on the body of the screw engage with the female threads formed in the screw hole of the vane body. The tip surface of the screw abuts against the bottom surface of the screw hole.
[0012] Embodiment 8 is based on the rotary compressor described in any one of Embodiments 1 to 7. The direction in which the vane body and the bush are aligned is defined as the second direction, and the bush side of the vane body is defined as the first side in the second direction. The roller piston has a lubricating oil supply passage that penetrates radially and opens into the groove. The bush has a bush recess on the first side in the second direction, where the distance from the central axis of the second cylindrical surface is smaller than the radius of curvature of the second cylindrical surface. The lubricating oil supply passage opens into the bush recess.
[0013] Embodiment 9 is based on the rotary compressor described in any one of embodiments 1 to 8. The roller piston is made of aluminum or an aluminum alloy.
[0014] The refrigeration cycle device of the embodiment includes a rotary compressor as described in any one of embodiments 1 to 8, a heat sink connected to the rotary compressor, an expansion device connected to the heat sink, and a heat absorber connected to the expansion device. [Brief explanation of the drawing]
[0015] [Figure 1] Circuit diagram of the refrigeration cycle device and cross-sectional view of the rotary compressor in the embodiment. [Figure 2] Cross-sectional view of the compression mechanism portion taken along line II-II of FIG. 1. [Figure 3] Enlarged view of the periphery of the bush in FIG. 2. [Figure 4] Enlarged view of the bush in FIG. 2. [Figure 5] Exploded perspective view of the vane. [Figure 6] Cross-sectional view taken along line VI-VI of FIG. 5. [Figure 7] Cross-sectional view taken along line VII-VII of FIG. 5. [Figure 8] Cross-sectional view taken along line VIII-VIII of FIG. 3. [Figure 9] Enlarged view of the periphery of the pin in FIG. 8. [Figure 10] Enlarged view of the periphery of the screw in FIG. 8.
Mode for Carrying Out the Invention
[0016] Hereinafter, the rotary compressor and the refrigeration cycle device of the embodiment will be described with reference to the drawings. FIG. 1 includes a circuit diagram of the refrigeration cycle device 1 in the embodiment. The refrigeration cycle device 1 includes 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 for circulating a refrigerant (fluid) through these components. The refrigerant circulates through the refrigeration cycle device 1 while undergoing a phase change.
[0017] The rotary compressor 10 compresses the low-pressure gaseous refrigerant taken into it to a high-temperature and high-pressure gaseous refrigerant. An accumulator (gas-liquid separator) 2b is arranged on the upstream side of the rotary compressor 10. The accumulator 2b separates the gas-liquid two-phase refrigerant and supplies the gaseous refrigerant to the rotary compressor 10.
[0018] The four-way valve 3 reverses the direction of refrigerant flow in the refrigerant flow path 8 of the first heat exchanger 4, expansion device 5, and second heat exchanger 6. When the four-way valve 3 is in the state shown in Figure 1, the refrigerant discharged from the rotary compressor 10 flows in the order of first heat exchanger 4, expansion device 5, and second heat exchanger 6. At this time, the first heat exchanger 4 functions as a condenser (heat sink), and the second heat exchanger 6 functions as an evaporator (heat absorber). When the four-way valve 3 switches from the state shown in Figure 1, the refrigerant discharged from the rotary compressor 10 flows through the second heat exchanger 6, the expansion device 5, and the first heat exchanger 4 in that order. At this time, the second heat exchanger 6 functions as a condenser (heat radiator), and the first heat exchanger 4 functions as an evaporator (heat absorber).
[0019] The condenser dissipates heat from the high-temperature, high-pressure gaseous refrigerant discharged from the rotary compressor 10, converting the high-temperature, high-pressure gaseous refrigerant into a high-pressure liquid refrigerant. The expansion device 5 reduces the pressure of the high-pressure liquid refrigerant supplied from the condenser, converting 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. The evaporator converts the gas-liquid two-phase refrigerant supplied from the expansion device 5 into a low-pressure gaseous refrigerant. In the evaporator, the low-pressure gas-liquid two-phase refrigerant absorbs heat of vaporization from the surroundings as it vaporizes, thus cooling the surroundings. The low-pressure gaseous refrigerant that has passed through the evaporator is taken into the rotary compressor 10 described above via the accumulator 2b.
[0020] In this way, in the refrigeration cycle device 1, the working fluid, the refrigerant, circulates while undergoing a phase change between gas and liquid. The refrigerant releases heat during the phase change from gas to liquid and absorbs heat during the phase change from liquid to gas. The refrigeration cycle device 1 uses the heat release or absorption of the refrigerant to perform heating, cooling, defrosting, etc.
[0021] Figure 1 includes a cross-sectional view of the rotary compressor 10 in an embodiment. The cross-sectional view of the rotary compressor 10 is shown along line II in Figure 2. Figure 2 is a cross-sectional view of the compression mechanism 20 along line II-II in Figure 1.
[0022] 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 case 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 case 11. The +R direction is the direction outward from the radial direction. The θ direction is the circumferential direction of the case 11. The +θ direction is the rotational direction of the right-hand screw that advances in the +T direction. The opposite directions of the +T, +R, and +θ directions are denoted as the -T, -R, and -θ directions, respectively.
[0023] As shown in Figure 1, the rotary compressor 10 includes a case 11, an electric motor unit 14, a shaft 15, a first bearing 30, a second bearing 35, a partition plate 33, a compression mechanism unit 20, a first muffler 38a, and a second muffler 38b.
[0024] The case 11 is formed in a cylindrical shape with both ends closed. The case 11 houses the electric motor 14, the shaft 15, and the compression mechanism 20. Inside the case 11, in the -T direction, lubricating oil 12 for lubricating the compression mechanism 20 is contained. Inside the case 11, in the +T direction, gaseous refrigerant compressed by the compression mechanism 20 is contained. The gaseous refrigerant and lubricating oil inside the case 11 are under high pressure. The gaseous refrigerant is supplied to the four-way valve 3 from the discharge port 13 in the +T direction of the case 11 through the refrigerant flow path 8.
[0025] The motor unit 14 is located inside the case 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 case 11. The rotor 14b is located in the -R direction relative to the stator 14a.
[0026] The shaft 15 is arranged coaxially with the case 11. The rotor 14b of the motor unit 14 is fixed to the shaft 15 in the +T direction. 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 case 11.
[0027] The first bearing (main bearing) 30 is positioned in the +T direction of the compression mechanism 20. The first bearing 30 has a bearing portion 31 and a closing portion 32. The bearing portion 31 of the first bearing 30 rotatably supports the shaft 15 of the compression mechanism 20 in the +T direction. The closing portion 32 of the first bearing 30 closes the opening of the compression mechanism 20 in the +T direction.
[0028] The second bearing (sub-bearing) 35 is positioned in the -T direction of the compression mechanism 20. The second bearing 35 has a bearing portion 36 and a closing portion 37. The bearing portion 36 of the second bearing 35 rotatably supports the shaft 15 in the -T direction of the compression mechanism 20. The closing portion 37 of the second bearing 35 closes the opening in the -T direction of the compression mechanism 20.
[0029] The compression mechanism 20 is located in the -T direction inside the case 11. The compression mechanism 20 may be a single-cylinder compression mechanism having one cylinder chamber 22, or a multi-cylinder compression mechanism having multiple cylinder chambers 22. In the example in Figure 1, the compression mechanism 20 has two cylinder chambers 22 aligned in the T direction. The partition plate 33 is positioned between the two cylinder chambers 22.
[0030] The compression mechanism 20 includes, for each cylinder, a cylinder 21, a roller piston 40, and a vane (blade) 50 (see Figure 2).
[0031] The cylinder 21 is positioned coaxially with the case 11. The cylinder 21 is fixed to the inner circumferential surface of the case 11. As shown in Figure 2, the cylinder 21 has a cylinder chamber 22. The cylinder chamber 22 is formed inside a through hole that penetrates the cylinder 21 in the T direction. The cylinder chamber 22 is formed coaxially with the case 11. The eccentric portion 16 of the shaft 15 is positioned inside the cylinder chamber 22.
[0032] The roller piston 40 is formed in a cylindrical shape. The roller piston 40 is arranged coaxially with the eccentric portion 16. The roller piston 40 is rotatable around the eccentric portion 16. A portion of the outer circumferential surface of the roller piston 40 is in contact with the inner circumferential surface of the cylinder 21 (the side surface of the cylinder chamber 22) via an oil film (oil surface) of several micrometers to several tens of micrometers. The space between the outer circumferential surface of the roller piston 40 and the inner circumferential surface of the cylinder 21 functions as the actual cylinder chamber 22.
[0033] The cylinder 21 has a refrigerant suction port 25 and a refrigerant discharge port 26. The suction port 25 penetrates the case 11 and the cylinder 21 in the R direction. The suction port 25 introduces the gaseous refrigerant supplied from the accumulator 2b shown in Figure 1 into the cylinder chamber 22.
[0034] The discharge port 26 penetrates the closure portion 32 of the first bearing 30 or the closure portion 37 of the second bearing 35 in the T direction. A reed valve is positioned on the opposite side of the cylinder chamber 22 from the discharge port 26. The reed valve opens and closes the discharge port 26 in accordance with the pressure in the cylinder chamber 22. The discharge port 26 discharges the gaseous refrigerant compressed in the cylinder chamber 22 to the outside of the cylinder chamber 22.
[0035] As shown in Figure 2, the vane 50 is housed in a slit 27 formed in the cylinder 21. The slit 27 penetrates the cylinder 21 in the T direction. The slit 27 extends, for example, along the R direction. The -R end of the slit 27 opens into the cylinder chamber 22. A back pressure chamber 28 is formed at the +R end of the slit. High-pressure lubricating oil 12 (see Figure 1) enters the back pressure chamber 28. The pressure of the lubricating oil 12 in the back pressure chamber 28 presses the vane 50 in the -R direction.
[0036] The tip of the vane 50 in the -R direction is hinged to the roller piston 40. As the shaft 15 rotates, the eccentric portion 16 and the roller piston 40 revolve (eccentrically rotate) in the θ direction inside the cylinder chamber 22. As the roller piston 40 revolves, the vane 50 moves back and forth in the R direction. The vane 50 divides the inside of the cylinder chamber 22 into a suction chamber 23 on the suction hole 25 side and a compression chamber 24 on the discharge hole 26 side.
[0037] As shown in Figure 1, the first muffler 38a is positioned in the +T direction of the closed portion 32 of the first bearing 30. A first muffler chamber is formed between the first muffler 38a and the first bearing 30. The first muffler chamber contains the high-pressure gaseous refrigerant discharged from the discharge hole 26 of the first bearing 30. The second muffler 38b is positioned in the -T direction of the closed portion 37 of the second bearing 35. A second muffler chamber is formed between the second muffler 38b and the second bearing 35. The second muffler chamber contains the high-pressure gaseous refrigerant discharged from the discharge hole 26 of the second bearing 35. The gaseous refrigerant in the second muffler chamber moves to the first muffler chamber through a through-hole (not shown) that penetrates the cylinder 21 in the T direction. The gaseous refrigerant in the first muffler chamber is discharged into the case 11 from the opening of the first muffler 38a.
[0038] I will explain the vane 50 in detail. Figure 3 is an enlarged view of the area around the bush 60 in Figure 2. A groove 42 is formed on the outer circumference of the roller piston 40. The groove 42 penetrates the roller piston 40 in the T direction. The inner surface of the groove 42 is a first cylindrical surface 42c extending in the T direction. The opening width of the groove 42 is smaller than the diameter of the bush 60, which will be described next.
[0039] As shown in Figure 2, the vane 50 has a vane body 51 and a bush 60. The vane body 51 is formed in a flat plate shape from a metal material such as iron, aluminum, or an aluminum alloy. Alternatively, resin, ceramic, or composite materials containing these materials may be used. The vane body 51 is housed in the slit 27 of the cylinder 21. As shown in Figure 3, a bush 60 is attached to the first surface 51s of the vane body 51's -R direction tip.
[0040] In this application, the Z, X, and Y directions of the Cartesian coordinate system are defined as follows as the local coordinate system of the vane 50. The Z direction is the height direction of the vane 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 roller piston 40. The X direction is the length direction of the vane 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 vane body 51 and the bush 60 are aligned. The +X direction (first side of the second direction) is the bush 60 side of the vane body 51. The -X direction (second side of the second direction) is the vane body 51 side of the bush 60. The Y direction is the width direction of the vane body 51. For example, the Y direction corresponds to the tangential direction of the θ direction. The opposite directions of the +Z, +X, and +Y directions are denoted as the -Z, -X, and -Y directions, respectively.
[0041] Figure 4 is an enlarged view of the bush 60 in Figure 2. The bush 60 is formed from a metallic material such as high-speed tool steel. High-speed tool steel is easy to process and has excellent wear resistance. As shown in Figure 4, the bush 60 has a second cylindrical surface 60c. The second cylindrical surface 60c slides against the first cylindrical surface 42c (see Figure 3) of the groove 42 of the roller piston 40. The bush 60 has a second surface 60s in the -X direction. As shown in Figure 6, at the mounting portion 50m between the vane body 51 and the bush 60, the first surface 51s of the vane body 51 and the second surface 60s of the bush 60 are positioned opposite each other. For example, the second surface 60s is flat. As shown in Figure 4, the bush 60 has a bush recess 64 in the +X direction. The bush recess 64 is recessed toward the central axis 61 from a virtual plane extended from the second cylindrical surface 60c. For example, the bottom surface 63 of the bush recess 64 is flat.
[0042] The bush 60 is formed within a range where the distance from the central axis 61 of the second cylindrical surface 60c is less than or equal to the radius of curvature 62 of the second cylindrical surface 60c. The bush 60 does not have any portion whose distance from the central axis 61 exceeds the radius of curvature 62. Therefore, the bush 60 can be manufactured as follows. First, a cylindrical intermediate material is formed by cutting or grinding while rotating the base material using a lathe or the like. The outer circumference of the intermediate material corresponds to the second cylindrical surface 60c. Next, the intermediate material is cut using a milling machine or the like to form the second surface 60s in the -X direction and the bottom surface 63 of the bush recess 64 in the +X direction. Since the bush 60 can be manufactured in this way, the manufacturing cost of the bush 60 is suppressed. Moreover, the accuracy of the dimensions, surface roughness, and cylindricity of the second cylindrical surface 60c is improved.
[0043] Figure 5 is an exploded perspective view of the vane 50. As described above, the vane 50 divides the cylinder chamber 22 into a suction chamber 23 and a compression chamber 24. The vane body 51 has a recess 52 extending from the first surface 51s in the +X direction to the side facing the suction chamber 23. The recess 52 opens to the suction chamber 23 side of the vane body 51 but not to the compression chamber 24 side. 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 first surface 51s on the compression chamber 24 side in the Y direction, and at the center and both ends in the Z direction. The area of the first surface 51s where the recesses 52 are not formed is a plane. That is, a plane extending over the entire Z direction is formed at the end of the first surface 51s on the compression chamber 24 side. The recesses 52 may be formed continuously over the entire Z direction on the suction chamber 23 side of the first surface 51s.
[0044] Figure 6 is a cross-sectional view along the line VI-VI in Figure 5 (the non-formed region of the recess 52). As previously mentioned, the second surface 60s of the bush 60 in the -X direction is planar. The first surface 51s of the vane body 51 in the +X direction is planar in the non-formed region of the recess 52. In the non-formed region of the recess 52, the first surface 51s of the vane body 51 and the second surface 60s of the bush 60 are in surface contact. 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.
[0045] Figure 7 is a cross-sectional view along line VII-VII in Figure 5 (the region where the recess 52 is formed). As mentioned above, the recess 52 opens to the suction chamber 23 side of the vane body 51 and does not open to 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 vane body 51 and the second surface 60s of the bush 60 are separated. 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.
[0046] Thus, in at least a portion of the mounting portion 50m in the Z direction, 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. The first surface 51s of the vane body 51 in the +X direction is subjected to the low pressure of the gaseous refrigerant in the suction chamber 23. As shown in Figure 2, the end face of the vane body 51 in the -X direction is subjected to the high pressure of the lubricating oil in the back pressure chamber 28. This causes the vane body 51 to be pressed towards the bush 60 in the +X direction. Separation between the vane body 51 and the bush 60 (vane jumping) is suppressed. Consequently, the generation of abnormal noise due to re-contact between the vane body 51 and the bush 60 is suppressed. In addition, leakage of gaseous refrigerant from the compression chamber 24 to the suction chamber 23 is suppressed.
[0047] In this embodiment, a recess 52 opening to the suction chamber 23 is formed on the first surface 51s of the vane body 51. Alternatively, a recess opening to the suction chamber 23 may be formed on the second surface 60s of the bush 60. Or, recesses opening to the suction chamber 23 may be formed on both the first surface 51s and the second surface 60s. In these cases as well, in at least a portion of the mounting portion 50m in the Z direction, 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.
[0048] In this embodiment, the non-formed region of the recess 52 on the first surface 51s of the vane body 51 and the second surface 60s of the bush 60 are both flat. In contrast, the first surface 51s and the second surface 60s in the non-formed region of the recess 52 may both be curved surfaces of the same shape. As a result, the first surface 51s and the second surface 60s are positioned opposite each other and in surface contact in the non-formed region of the recess.
[0049] As shown in Figure 5, the vane 50 has a screw 70 and a pair of pins 78. Figure 8 is a cross-sectional view along line VIII-VIII in Figure 3. The screw 70 is located in the center of the mounting portion 50m in the Z direction. The pair of pins 78 are located separately in the +Z and -Z directions of the mounting portion 50m. The central axes of the screw 70 and the pair of pins 78 are aligned along the X direction.
[0050] Figure 9 is a magnified view of the area around pin 78 in Figure 8. Pin 78 is cylindrical in shape. Pin 78 may be a solid rod or a spring pin. A first hole 58 is formed on the first surface 51s of the vane body 51. A second hole 68 is formed on the second surface 60s of the bush 60. Both the first hole 58 and the second hole 68 are cylindrical in shape. The central axes of the first hole 58 and the second hole 68 are aligned in the X direction. Pin 78 is inserted across both the first hole 58 and the second hole 68. This suppresses misalignment in the Y direction between the vane body 51 and the bush 60.
[0051] The diameter of one of the first hole 58 and the second hole 68 is larger than the diameter of the other, and is also larger than the diameter of the pin 78. In the example in Figure 9, the diameter of the first hole 58 is larger than the diameter of the second hole 68, and is also larger than the diameter of the pin 78. The diameter of the second hole 68 is less than or equal to the diameter of the pin 78. The pin 78 is press-fitted into the second hole 68. This prevents the pin 78 from falling out. The pin 78 is not press-fitted into the first hole 58. This makes it easy to assemble the vane body 51 and the bush 60. There is a gap between the -X end of the pin 78 and the bottom of the first hole 58.
[0052] The pin 78 is press-fitted into the second hole 68 of the bush 60, but not into the first hole 58 of the vane body 51. The size of the bush 60 in the X direction is smaller than that of the vane body 51. Press-fitting the pin 78 into the second hole 68 of the bush 60 in the X direction is easier than press-fitting it into the first hole 58 of the vane body 51.
[0053] Figure 10 is an enlarged view of the area around the screw 70 in Figure 8. The screw 70 is a restricting member that restricts the vane body 51 from moving away from the bush 60 in the -X direction. A rivet or the like may be used as the restricting member instead of the screw 70. The 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. A male thread 73 is formed in the middle of the body 72 in the X direction.
[0054] As described above, a bush recess 64 is formed in the +X direction of the bush 60. A counterbore hole 65 is formed in the bottom surface 63 of the bush recess 64. The head 71 of the screw 70 is housed inside the counterbore hole 65. The diameter of the counterbore hole 65 is larger than the diameter of the head 71. A gap exists between the bottom surface of the counterbore hole 65 and the head 71. A through hole is formed from the bottom surface of the counterbore hole 65 to the second surface 60s of the bush 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.
[0055] A cylindrical screw hole 55 is formed on the first surface 51s of the vane body 51. A female thread 53 is formed in the region of the screw hole 55 in the +X direction. The male thread 73 of the screw 70 engages with the female thread 53 of the screw hole 55. As a result, the screw 70 restricts the vane body 51 from moving away from the bush 60 in the -X direction. The compression mechanism 20 shown in Figure 2 does not have a biasing member that biases the vane body 51 toward the bush 60 in the +X direction. Even in this case, the vane body 51 is prevented from moving away from the bush 60 in the -X direction. Since there is no biasing member, the inner diameter of the cylinder 21 can be enlarged. As a result, the height of the cylinder 21 can be reduced, and the rotary compressor 10 can be miniaturized.
[0056] The female thread 53 is formed only in the region of the screw hole 55 in the +X direction. The female thread 53 is not formed in the region of the screw hole 55 in the -X direction. The diameter of the screw hole 55 is larger than the diameter of the body 72 of the screw 70. The bottom surface 56 of the screw hole 55 and the tip surface 76 of the screw 70 are both flat. The tip surface 76 of the screw 70 abuts against the bottom surface 56 of the screw hole 55. This allows the screw 70 to be accurately positioned in a predetermined location in the X direction. A small gap is maintained between the head 71 of the screw 70 and the bottom surface of the counterbore hole 65. The size of the gap can be minimized, and the distance of the vane body 51 from the bush 60 can be minimized.
[0057] As shown in Figure 9, the diameter of the first hole 58 in the vane body 51 is larger than the diameter of the pin 78 pressed into the bush 60. The vane body 51 and the bush 60 are relative to each other in the Z direction, to the extent of the clearance between the first hole 58 and the pin 78. The screw 70 allows relative movement between the vane body 51 and the bush 60 in the Z direction.
[0058] The height of the vane body 51 and the bush 60 in the Z direction is slightly less than the height of the cylinder 21 in the Z direction. This allows the vane body 51 and the bush 60 to move within the cylinder chamber 22. If the vane body 51 and the bush 60 were rigidly joined by a screw 70, the bush 60 might be fixed in a position where it protrudes from the vane body 51 to one side in the Z direction. In this case, it would be necessary to remove the protruding portion of the bush 60 while the vane body 51 and the bush 60 are rigidly joined.
[0059] In contrast, the vane body 51 and bush 60 of this embodiment are relatively movable in the Z direction. The vane body 51 and bush 60 are not fixed in a misaligned state in the Z direction. With the vane body 51 and bush 60 rigidly joined, there is no need to process the protruding portion of the bush 60. Therefore, the manufacturing cost of the rotary compressor is reduced.
[0060] As shown in Figure 3, the bush 60 is housed in the groove 42 of the roller piston 40. The first cylindrical surface 42c of the groove 42 and the second cylindrical surface 60c of the bush 60 are coaxially arranged and slide against each other. This hinges the +X end of the vane 50 to the roller piston 40.
[0061] As mentioned above, lubricating oil 12 is contained in the lower part of the case 11 shown in Figure 1. A first oil supply passage 17 is formed inside the shaft 15 along its central axis. A pumping mechanism (not shown), such as a torsion plate, is provided inside the first oil supply passage 17. As the shaft 15 rotates, the pumping mechanism draws the lubricating oil 12 upward from the lower part of the case 11. A second oil supply passage 18 is formed extending radially through the shaft 15 from the first oil supply passage 17 to the outer circumference of the shaft 15. The lubricating oil 12 passes through the second oil supply passage 18 and is supplied to the sliding parts between the eccentric part 16 and the roller piston 40, etc.
[0062] As shown in Figure 3, the roller piston 40 has a lubricating oil supply passage 44. The lubricating oil supply passage 44 penetrates the roller piston 40 radially and opens into the groove 42. As previously mentioned, the bush 60 has a bush recess 64 in the +X direction. The lubricating oil supply passage 44 opens into the bush recess 64. The lubricating oil 12 passes through the lubricating oil supply passage 44 and is stored in the bush recess 64. The lubricating oil 12 is supplied from the bush recess 64 to the sliding part between the groove 42 and the bush 60. This allows the hinge connection between the roller piston 40 and the vane 50 to operate smoothly.
[0063] Accordingly, the roller piston 40 can be made from materials such as aluminum or aluminum alloy. The vane body 51 can also be made from materials such as aluminum or aluminum alloy. This reduces the weight of the rotary compressor 10. Furthermore, vibrations associated with the eccentric rotation of the eccentric section 16 and the roller piston 40 are suppressed. The weight of the balancer attached to the shaft 15 to reduce vibrations can also be reduced.
[0064] As detailed above, the rotary compressor 10 of the embodiment includes a cylinder 21, a shaft 15, a roller piston 40, and vanes 50. The cylinder 21 has a cylindrical cylinder chamber 22 that compresses fluid drawn in from the suction hole 25 and discharges it from the discharge hole 26. The shaft 15 is arranged coaxially with the cylinder chamber 22 and has an eccentric portion 16 inside the cylinder chamber 22 that is eccentric from the central axis of the cylinder chamber 22. The roller piston 40 is formed in a cylindrical shape, arranged coaxially with the eccentric portion 16, is rotatable around the eccentric portion 16, and can contact the side surface of the cylinder chamber 22 via an oil film. The vanes 50 are housed in a slit 27 of the cylinder 21, and their ends on the cylinder chamber 22 side are hinged to the roller piston 40, dividing the cylinder chamber 22 into a suction chamber 23 on the suction hole 25 side and a compression chamber 24 on the discharge hole 26 side. The direction of the central axis of the roller piston 40 is the Z direction. A groove 42 having a first cylindrical surface 42c extending in the Z direction is formed on the outer circumference of the roller piston 40. The vane 50 has a vane body 51 and a bush 60. The bush 60 is mounted on the tip of the vane body 51 on the cylinder chamber 22 side and is housed in the groove 42 to form a hinge connection. The bush 60 has a second cylindrical surface 60c that slides with the first cylindrical surface 42c. The bush 60 is formed within a range where the distance from the central axis of the second cylindrical surface 60c is less than or equal to the radius of curvature 62 of the second cylindrical surface 60c. With this configuration, the second cylindrical surface 60c of the bush 60 can be formed by cutting the base material while it is rotating. Therefore, the cost of the rotary compressor 10 can be reduced.
[0065] At the mounting portion 50m between the vane body 51 and the bush 60, the first surface 51s of the vane body 51 and the second surface 60s of the bush 60 are arranged facing 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. In this configuration, the low pressure of the gaseous refrigerant in the suction chamber 23 acts on the first surface 51s of the vane body 51 in the +X direction. On the other hand, the high pressure of the lubricating oil in the back pressure chamber 28 acts on the end face of the vane body 51 in the -X direction. As a result, the vane body 51 is pressed towards the bush 60 in the +X direction. Separation between the vane body 51 and the bush 60 is suppressed.
[0066] 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 inserted across both the first hole 58 and the second hole 68. This suppresses misalignment in the Y direction between the vane body 51 and the bush 60.
[0067] The diameter of one of the first hole 58 and the second hole 68 is greater than the diameter of the other, and is also greater than the diameter of the pin 78. This prevents the pin 78 from falling out. Furthermore, assembly of the vane body 51 and the bush 60 is easier.
[0068] The direction in which the vane body 51 and the bush 60 are aligned is defined as the X direction, the direction of the vane body 51 toward the bush 60 is defined as the +X direction, and the direction of the bush 60 toward the vane body 51 is defined as the -X direction. The vane body 51 has a screw 70 that restricts it from moving away from the bush 60 in the -X direction. There is no biasing member that biases the vane body 51 toward the bush 60 in the +X direction. Since there is no biasing member, the inner diameter of the cylinder 21 can be enlarged. This makes it possible to reduce the height of the cylinder 21, and the rotary compressor 10 can be made more compact.
[0069] The screw 70 allows relative movement in the Z direction between the vane body 51 and the bush 60. As a result, the vane body 51 and the bush 60 are not fixed in a misaligned state in the Z direction. Processing to remove the portion of the bush 60 protruding from the vane body 51 is unnecessary. Therefore, the manufacturing cost of the rotary compressor is reduced.
[0070] The head 71 of the screw 70 is housed in a counterbore 65 formed in the +X direction of the bush 60. The male thread 73 formed on the body 72 of the screw 70 engages with the female thread 53 formed in the screw hole 55 of the vane body 51. The tip surface 76 of the screw 70 abuts against the bottom surface 56 of the screw hole 55. This ensures that the screw 70 is precisely positioned in the predetermined location in the X direction. A small gap is maintained between the head 71 of the screw 70 and the bottom surface of the counterbore 65. The size of this gap can be minimized, thereby minimizing the distance between the vane body 51 and the bush 60.
[0071] The direction in which the vane body 51 and the bush 60 are aligned is defined as the X direction, and the direction of the vane body 51 toward the bush 60 is defined as the +X direction. The roller piston 40 has a lubricating oil supply passage 44 that penetrates radially and opens into the groove 42. The bush 60 has a bush recess 64 in the +X direction, the distance from the central axis of the second cylindrical surface 60c being less than the radius of curvature 62 of the second cylindrical surface 60c. The lubricating oil supply passage 44 opens into the bush recess 64. The lubricating oil 12 passes through the lubricating oil supply passage 44 and is stored in the bush recess 64. The lubricating oil 12 is supplied from the bush recess 64 to the sliding surface between the groove 42 and the bush 60. This allows the hinge connection between the roller piston 40 and the vane 50 to operate smoothly. Furthermore, the lubrication oil supply passage 44 formed in the roller piston 40 may be a groove formed on the axial end face of the roller piston 40 instead of a through hole. In particular, by forming the lubrication oil supply passage 44 as a groove on the axial end face of the roller piston 40, or as a through hole formed at a position close to the axial end face, the second oil supply passage 18, the axial end face of the eccentric portion 16, and the lubrication oil supply passage 44 can be kept in constant communication. As a result, refrigeration oil can be supplied to the bush 60 side at all times when the rotary compressor 10 is in operation without requiring any extra processing of the eccentric portion 16.
[0072] The roller piston 40 is made of aluminum or an aluminum alloy. This reduces the weight of the rotary compressor 10.
[0073] The refrigeration cycle device 1 of this embodiment includes the rotary compressor 10 described above, one of the first heat exchanger 4 and the second heat exchanger 6 which functions as a radiator, an expansion device 5, and the other of the first heat exchanger 4 and the second heat exchanger 6 which functions as a heat absorber. The radiator is connected to the rotary compressor 10. The expansion device 5 is connected to the radiator. The heat absorber is connected to the expansion device 5. By having the aforementioned rotary compressor 10, the cost of the refrigeration cycle device 1 can be reduced.
[0074] According to at least one embodiment described above, the bush 60 is formed within a range where the distance from the central axis of the second cylindrical surface 60c is within the radius of curvature 62 of the second cylindrical surface 60c. This makes it possible to reduce the cost of the rotary compressor 10.
[0075] While several embodiments of the present invention have been described, these embodiments are presented as examples only and are not intended to limit the scope of the invention. These embodiments can be carried out in a variety of other forms, 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, as well as in the claims and their equivalents. [Explanation of symbols]
[0076] G...interval, 1...refrigeration cycle device, 4...first heat exchanger (radiator, heat absorber), 5...expansion device, 6...second heat exchanger (heat absorber, heat absorber), 10...rotary compressor, 15...shaft, 16...eccentric section, 21...cylinder, 22...cylinder chamber, 23...suction chamber, 24...compression chamber, 25...suction port, 26...discharge port, 27...slit, 40...roller piston, 42...groove, 42c...first cylindrical surface 44... Lubrication oil supply channel, 50... Vane, 50m... Mounting part, 51... Vane body, 51s... First surface, 53... Female thread, 55... Screw hole, 56... Bottom surface, 58... First hole, 60... Bushing, 60s... Second surface, 61... Central axis, 62... Radius of curvature, 64... Bushing recess, 65... Counterbore hole, 70... Screw (regulating member), 71... Head, 72... Body, 73... Male thread, 76... Tip surface, 78... Pin.
Claims
1. A cylinder having a cylindrical cylinder chamber that compresses a fluid drawn in through an intake port and discharges it through a discharge port, A shaft arranged coaxially with the cylinder chamber and having an eccentric portion inside the cylinder chamber that is eccentric from the central axis of the cylinder chamber, A roller piston formed in a cylindrical shape, arranged coaxially with the eccentric portion, rotatable around the eccentric portion, and capable of contacting the side surface of the cylinder chamber via the oil surface, The cylinder has a vane housed in a slit, the tip of which is hinged to the roller piston on the cylinder chamber side, and which divides the cylinder chamber into a suction chamber on the suction hole side and a compression chamber on the discharge hole side. When the direction of the central axis of the roller piston is defined as the first direction, a groove having a first cylindrical surface extending in the first direction is formed on the outer circumference of the roller piston. The vane comprises a vane body and a bush that is attached to the tip of the vane body on the cylinder chamber side and housed in the groove to constitute the hinge connection. The bush has a second cylindrical surface that slides against the first cylindrical surface, The bush is formed within a range where the distance from the central axis of the second cylindrical surface is less than or equal to the radius of curvature of the second cylindrical surface. Rotary compressor.
2. In the mounting portion between the vane body and the bush, the first surface of the vane body and the second surface of the bush are arranged facing 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. The rotary compressor according to claim 1.
3. A cylindrical first hole is formed on the first surface, and a cylindrical second hole is formed on the second surface. A cylindrical pin is inserted across both the first hole and the second hole, The rotary compressor according to claim 2.
4. The diameter of one of the first hole and the second hole is greater than the diameter of the other, and is also greater than the diameter of the pin. The rotary compressor according to claim 3.
5. When the direction in which the vane body and the bush are aligned is defined as the second direction, the bush side of the vane body is defined as the first side in the second direction, and the vane body side of the bush is defined as the second side in the second direction, The vane body has a restricting member that restricts it from moving away from the bush towards the second side in the second direction, The vane body does not have a biasing member that biases it toward the bush towards the first side in the second direction. The rotary compressor according to claim 4.
6. The restricting member allows relative movement between the vane body and the bush in the first direction. The rotary compressor according to claim 5.
7. The aforementioned regulating member is a screw, The head of the screw is housed in a counterbore formed on the first side of the bush in the second direction. The male thread formed on the body of the screw is threaded into the female thread formed in the screw hole of the vane body. The tip surface of the screw abuts against the bottom surface of the screw hole. The rotary compressor according to claim 6.
8. When the direction in which the vane body and the bush are aligned is defined as the second direction, and the bush side of the vane body is defined as the first side in the second direction, The roller piston has a lubricating oil supply passage that penetrates radially and opens into the groove, The bush has a bush 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 lubrication oil supply passage opens into the bush recess, The rotary compressor according to claim 1.
9. The roller piston is made of aluminum or an aluminum alloy. A rotary compressor according to claim 1 or 8.
10. A rotary compressor according to claim 1 or 2, A heat sink connected to the rotary compressor, An expansion device connected to the heat sink, The expansion device has a heat absorber connected to it, Refrigeration cycle device.