Scroll compressor and refrigeration device

Abstract

A compression mechanism (40) of a scroll compressor (10) has a stationary scroll (60) and an orbiting scroll (70). An oil groove (80) is formed in an opposing surface (66) of an outer peripheral wall (63) of the stationary scroll (60), the opposing surface (66) facing the front surface of a rotation-side end plate (71) of the rotation scroll (70), and high-pressure lubricating oil corresponding to the discharge pressure of the compression mechanism (40) is supplied to the oil groove (80). The oil groove (80) has a circumferential groove portion (81) extending in the circumferential direction, and a radial groove portion (82) extending radially outward of the stationary scroll plate (60) and communicating with the circumferential groove portion (81).

Description

Technical Field

[0001] The invention relates to a scroll compressor and a refrigeration device. Background Art

[0002] Patent Document 1 discloses a scroll compressor including a compression mechanism having a fixed scroll and a movable scroll (orbiting scroll) and a compression chamber formed between the two scrolls.

[0003] The compression mechanism of Patent Document 1 has an introduction mechanism and an auxiliary introduction mechanism for supplying the fluid in the compression chamber to the back pressure chamber formed on the back side of the movable scroll. The auxiliary introduction mechanism has an auxiliary introduction path that connects the compression chamber with the back pressure chamber and a check valve, and the check valve allows the fluid to flow from the compression chamber to the back pressure chamber and prohibits the fluid from flowing from the back pressure chamber to the compression chamber. In Patent Document 1, the movable scroll may tilt when the compressor is started and during transitional operation. When tilting occurs, the movable scroll is restored from the tilted state by the auxiliary introduction mechanism.

[0004] Prior art literature

[0005] Patent Literature

[0006] Patent Document 1: Japanese Patent Publication No. 2015-105642 Summary of the invention

[0007] -Technical problem to be solved by the invention-

[0008] In the scroll compressor of Patent Document 1, under certain operating conditions, it may be impossible to suppress the orbiting scroll from tilting.

[0009] An object of the present disclosure is to suppress the tilting of an orbiting scroll.

[0010] -Technical solutions for solving technical problems-

[0011] The first aspect of the present disclosure is directed to a scroll compressor 10. The scroll compressor 10 includes a housing 20 and a compression mechanism 40, wherein the compression mechanism 40 is accommodated in the housing 20 and includes a fixed scroll 60 and an orbiting scroll 70, wherein the fixed scroll 60 includes a fixed side end plate 61, an outer peripheral wall 63, and a fixed side scroll 62, wherein the outer peripheral wall 63 is disposed at the outer edge of the fixed side end plate 61, and the fixed side scroll 62 is spiral-shaped and disposed at the inner side of the outer peripheral wall 63, wherein the orbiting scroll 70 includes an orbiting side end plate 71 and an orbiting side scroll 72, wherein the front ends of the fixed side end plate 61 and the outer peripheral wall 63 are in sliding contact with the orbiting side end plate 71, and the orbiting side scroll 72 is disposed at the inner side of the outer peripheral wall 63, wherein the front ends of the fixed side end plate 61 and the outer peripheral wall 63 are in sliding contact with the orbiting side end plate 71, and the orbiting side scroll 72 is disposed at the inner side of the outer peripheral wall 63, and wherein the front ends of the fixed side end plate 61 and the outer peripheral wall 63 are in sliding contact with the orbiting side end plate 71. 2 is in a spiral shape, the revolving-side scroll 72 is arranged on the front surface of the revolving-side end plate 71 and meshes with the stationary-side scroll 62, an oil groove 80 is formed on the opposite surface 66 of the outer peripheral wall 63 opposite to the front surface of the revolving-side end plate 71, and high-pressure lubricating oil is supplied to the oil groove 80, the high pressure is equivalent to the discharge pressure of the compression mechanism 40, and the oil groove 80 has a circumferential groove portion 81 and a radial groove portion 82, the circumferential groove portion 81 extends along the circumference of the stationary scroll plate 60, and the radial groove portion 82 extends radially outward of the stationary scroll plate 60 and is communicated with the circumferential groove portion 81.

[0012] When the orbiting scroll 70 is in stable motion, the gap formed between the orbiting scroll 70 and the fixed scroll 60 is in a substantially uniform state. In contrast, if the orbiting scroll 70 is in an unstable motion, the orbiting scroll 70 tilts, so that the gap between the orbiting scroll 70 and the fixed scroll 60 has a relatively narrow portion and a relatively wide portion.

[0013] In the first aspect, since the oil groove 80 has the radial groove portion 82, when the orbiting scroll 70 begins to tilt, due to the pressure in the radial groove portion 82 supplied with high-pressure lubricating oil, a force that pulls the orbiting scroll 70 away from the fixed scroll 60 acts on the narrower portion of the gap between the orbiting scroll 70 and the fixed scroll 60. At this time, since the radial groove portion 82 extends radially outward of the fixed scroll 60, the high pressure acts on a position far from the center of gravity of the orbiting scroll 70. As a result, the torque that pulls the orbiting scroll 70 away from the fixed scroll 60 can be increased, and the gap between the orbiting scroll 70 and the fixed scroll 60 can be maintained in a uniform state. As a result, the movement of the orbiting scroll 70 can be maintained in a stable state, and the tilting state of the orbiting scroll 70 can be suppressed.

[0014] The second aspect is that, on the basis of the first aspect, the scroll compressor further includes a fixed component 50 and a sealing ring 57, wherein the fixed component 50 is arranged on the back side of the revolving scroll 70, a back pressure space 90 is formed between the fixed component 50 and the revolving scroll 70, and an annular ring groove 56 is formed on the surface of the fixed component 50 located on the revolving scroll 70 side, and the sealing ring 57 is accommodated in the ring groove 56, and the sealing ring 57 abuts against the back side of the revolving scroll 70, thereby The back pressure space 90 is divided into a first back pressure space 91 formed on the inner peripheral side of the annular groove 56 and a second back pressure space 92 formed on the outer peripheral side of the annular groove 56. The pressure in the first back pressure space 91 is equivalent to the discharge pressure of the compression mechanism 40. The pressure in the second back pressure space 92 is higher than the pressure of the fluid sucked into the compression mechanism 40 and lower than the pressure of the fluid discharged from the compression mechanism 40. When the revolving scroll 70 is tilted, the radial groove portion 82 is connected to the second back pressure space 92.

[0015] Here, the inclination of the orbiting scroll 70 is caused by the fact that the force that pushes up the back surface of the orbiting scroll 70 and presses the orbiting scroll 70 against the fixed scroll 60 is relatively insufficient compared to the force that pulls the orbiting scroll 70 and the fixed scroll 60 apart.

[0016] In the second aspect, when the orbiting scroll 70 tilts, since the radial groove 82 is connected to the second back pressure space 92, when the orbiting scroll 70 tilts, the high-pressure lubricating oil is supplied from the end of the radial groove 82 to the second back pressure space 92. As a result, the pressure in the second back pressure space 92 rises, and the force that pushes up the back side of the orbiting scroll 70 and presses the orbiting scroll 70 against the fixed scroll 60 increases. As a result, the orbiting scroll 70 can be restored from the tilted state as soon as possible.

[0017] According to a third aspect, based on the first aspect or the second aspect, the radial groove portion 82 is formed at an end portion of the circumferential groove portion 81 .

[0018] In the third aspect, since the radial groove portion 82 is formed at the end portion of the circumferential groove portion 81 , the lubricating oil can be sufficiently supplied to the end portion of the circumferential groove portion 81 .

[0019] According to a fourth aspect, in any one of the first to third aspects, a seal length L1 from an end of the radial groove portion 82 on the opposing surface 66 to an outer edge of the orbiting scroll 70 is 2 mm or more.

[0020] In the fourth aspect, since the seal length L1 is 2 mm or more, it is possible to suppress leakage of the high-pressure lubricating oil from the oil groove 80 while the orbiting scroll 70 is operating stably.

[0021] A fifth aspect is a refrigeration device including the scroll compressor (10) according to any one of the first to fourth aspects, and a refrigerant circuit (1a) through which the refrigerant compressed by the scroll compressor (10) flows.

[0022] In the fifth aspect, a refrigeration device (1) including the scroll compressor (10) can be provided, which can suppress the orbiting scroll (70) from tilting. BRIEF DESCRIPTION OF THE DRAWINGS

[0023] Figure 1 1 is a refrigerant circuit diagram showing the structure of the refrigeration device of the present embodiment;

[0024] Figure 2 is a longitudinal sectional view showing the structure of a scroll compressor;

[0025] Figure 3 It is a longitudinal cross-sectional view enlarging the periphery of the compression mechanism;

[0026] Figure 4 is a bottom view of the static scroll;

[0027] Figure 5 is a bottom view of the fixed scroll, and is an explanatory diagram showing the position of a sensor when measuring the movement of the orbiting scroll;

[0028] Figure 6 is a diagram showing the results of measuring the motion of the orbiting scroll;

[0029] Figure 7 It is a figure which shows the result of the edge collapse limit test. DETAILED DESCRIPTION

[0030] (Implementation Method)

[0031] The following is a detailed description of the embodiments of the present disclosure with reference to the accompanying drawings. It should be noted that the present disclosure is not limited to the embodiments shown below, and various changes can be made without departing from the technical concept of the present disclosure. The drawings are used to conceptually illustrate the present disclosure, so in order to facilitate understanding, the size, ratio or quantity is sometimes exaggerated or simplified as needed.

[0032] (1) Overview of Refrigeration Equipment

[0033] like Figure 1As shown, a scroll compressor 10 is provided in a refrigeration device 1. The refrigeration device 1 has a refrigerant circuit 1a filled with refrigerant. The refrigerant circuit 1a has a scroll compressor 10, a radiator 3, a decompression mechanism 4, and an evaporator 5. The decompression mechanism 4 is, for example, an expansion valve. The refrigerant circuit 1a performs a vapor compression refrigeration cycle.

[0034] The refrigeration device 1 is an air conditioning device. The air conditioning device may also be a dedicated refrigeration machine, a dedicated heating machine, or an air conditioning device that switches between refrigeration and heating. In this case, the air conditioning device has a switching mechanism (such as a four-way reversing valve) that switches the circulation direction of the refrigerant. The refrigeration device 1 may also be a water heater, a cooling unit, a cooling device that cools the air in a warehouse, etc. The cooling device cools the air inside a cold storage, a freezer, a container, etc.

[0035] (2) Compressor

[0036] The scroll compressor 10 includes a housing 20, a motor 30, a drive shaft 11, a compression mechanism 40, and a fixing member 50. Figure 2 As shown, the housing 20 accommodates the motor 30 , the drive shaft 11 , the compression mechanism 40 , and the fixing member 50 .

[0037] It should be noted that, in the following description, "axial direction" refers to the direction in which the drive shaft 11 extends, "radial direction" refers to the direction orthogonal to the axis of the drive shaft 11, and "circumferential direction" refers to the circumferential direction based on the axis of the drive shaft 11. "Radially inner side" refers to the side close to the axis of the drive shaft 11, and "radially outer side" refers to the side away from the axis of the drive shaft 11.

[0038] (2-1) Shell

[0039] The housing 20 is composed of a sealed container having a long longitudinal length. The housing 20 has a cylindrical body 20a extending in the up-down direction and two cover parts 20b that close the two ends of the body 20a. An oil storage part 21 is provided at the bottom of the housing 20. Lubricating oil is stored in the oil storage part 21. A suction pipe 12 is connected to the upper part of the housing 20. A discharge pipe 13 is connected to the body 20a of the housing 20.

[0040] (2-2) Electric motor

[0041] The motor 30 is arranged in the center of the housing 20. The motor 30 has a stator 31 and a rotor 32. The stator 31 is fixed to the inner peripheral surface of the housing 20. The rotor 32 is arranged inside the stator 31. The drive shaft 11 passes through the rotor 32. The rotor 32 is fixed to the drive shaft 11.

[0042] (2-3) Drive shaft

[0043] The drive shaft 11 extends in the up-down direction along the central axis of the housing 20. The drive shaft 11 includes a main shaft portion 14 and an eccentric portion 15.

[0044] The eccentric portion 15 is provided at the upper end of the main shaft portion 14. The outer diameter of the eccentric portion 15 is smaller than the outer diameter of the main shaft portion 14. The axis of the eccentric portion 15 is offset from the axis of the main shaft portion 14 by a predetermined distance.

[0045] The upper portion of the main shaft portion 14 passes through the fixing member 50 and is rotatably supported by an upper bearing 51 of the fixing member 50. The lower portion of the main shaft portion 14 is rotatably supported by a lower bearing 22 described later.

[0046] (2-4) Compression mechanism

[0047] The compression mechanism 40 is arranged on the upper side of the housing 20. Figure 2 and Figure 3 As shown, the compression mechanism 40 includes a fixed scroll 60 and an orbiting scroll 70. The fixed scroll 60 is fixed to the upper surface of the fixed member 50. The orbiting scroll 70 is arranged between the fixed scroll 60 and the fixed member 50. The orbiting scroll 70 meshes with the fixed scroll 60.

[0048] (2-4-1) Stationary Scroll

[0049] The fixed scroll (60) includes a fixed-side end plate (61), a fixed-side wrap (62), and an outer peripheral wall (63).

[0050] The stationary end plate 61 is formed in a disk shape. The stationary scroll 62 is formed in a spiral shape. The stationary scroll 62 extends from the front surface ( Figure 2 The stationary scroll 62 is arranged on the inner side of the outer peripheral wall 63 of the stationary end plate 61.

[0051] The outer peripheral wall 63 is formed in a substantially cylindrical shape. The outer peripheral wall 63 extends from the front surface ( Figure 2 The outer edge of the lower side of the scroll 62 protrudes downward. The outer peripheral wall 63 is provided to surround the outer peripheral side of the stationary scroll 62.

[0052] The front end surface of the stationary scroll 62 ( Figure 2 The bottom of the outer wall 63 and the front end surface of the outer wall 63 ( Figure 2 The outer peripheral wall 63 of the fixed scroll 60 is fixed to the upper surface of the fixed member 50.

[0053] (2-4-2) Orbiting Scroll

[0054] The orbiting scroll 70 includes an orbiting end plate 71 , an orbiting lap 72 , and a flange portion 73 . The orbiting end plate 71 is formed in a disk shape. The front ends of the stationary end plate 61 and the outer peripheral wall 63 are in sliding contact with the orbiting end plate 71 .

[0055] The revolving scroll 72 is formed in a spiral shape. Figure 2 The orbiting scroll 72 meshes with the stationary scroll 62.

[0056] The flange portion 73 is formed on the back side ( Figure 2 The eccentric portion 15 of the drive shaft 11 is inserted into the flange portion 73. Thus, the drive shaft 11 is connected to the orbiting scroll 70. In other words, the drive shaft 11 is connected to the compression mechanism 40.

[0057] (2-4-3) Inlet and outlet

[0058] A suction port 64 is formed in the outer peripheral wall 63 of the fixed scroll 60. The suction port 64 opens near the winding end of the fixed scroll 62. The suction port 64 is connected to the downstream end of the suction pipe 12.

[0059] A discharge port 65 is formed at the center of the stationary end plate 61 of the stationary scroll 60. The discharge port 65 opens on the upper surface of the stationary end plate 61 of the stationary scroll 60. The high-pressure gas refrigerant discharged from the discharge port 65 flows into the upper space 23 of the shell 20, and flows from the upper space 23 to the lower space 24 via a discharge passage (not shown) formed in the fixed member 50.

[0060] (2-4-4) Fluid Chamber

[0061] The compression mechanism 40 has a fluid chamber F into which the refrigerant flows. The fluid chamber F is formed between the fixed scroll 60 and the orbiting scroll 70. The orbiting-side lap 72 of the orbiting scroll 70 is arranged to mesh with the fixed-side lap 62 of the fixed scroll 60. The fluid chamber F is formed by the engagement of the fixed-side lap 62 with the orbiting-side lap 72, and the compression chamber S is formed by closing the fluid chamber F. The gaseous refrigerant is compressed in the compression chamber S.

[0062] Here, the front end surface ( Figure 2 The lower surface of the fixed scroll 60 is the opposite surface 66 of the front surface of the orbiting scroll 70. Figure 2 The upper surface of the orbiting scroll (70) becomes the opposite surface of the orbiting scroll (70) and the front end surface of the fixed scroll (60).

[0063] (2-5) Fixed parts

[0064] The fixing member 50 is disposed below the compression mechanism 40. Specifically, the fixing member 50 is disposed on the back side of the orbiting scroll 70. The fixing member 50 is disposed above the motor 30. Between the fixing member 50 and the motor 30, an inflow end of the discharge pipe 13 is disposed.

[0065] The fixing member 50 is formed into a cylindrical shape extending in the axial direction (vertical direction). The outer diameter of the upper portion of the fixing member 50 is formed to be larger than the outer diameter of the lower portion of the fixing member 50. The inner diameter of the upper portion of the fixing member 50 is formed to be larger than the inner diameter of the lower portion of the fixing member 50.

[0066] The fixed component 50 has an annular portion 52, a recessed portion 53 and an upper bearing 51. The annular portion 52 is a portion located on the upper side of the fixed component 50. The annular portion 52 is provided on the outer periphery of the fixed component 50. The recessed portion 53 is formed in the upper center of the fixed component 50. The recessed portion 53 is formed in a disk shape that is recessed downward. The recessed portion 53 forms a crankshaft chamber 54 that accommodates the flange portion 73 of the revolving scroll 70. The eccentric portion 15 rotates eccentrically in the crankshaft chamber 54. The upper bearing 51 is formed on the lower side of the fixed component 50. Specifically, the upper bearing 51 is formed below the recessed portion 53.

[0067] The fixing member 50 is fixed inside the housing 20 by being pressed in. Specifically, the outer peripheral surface of the annular portion 52 of the fixing member 50 is fixed to the inner peripheral surface of the trunk portion 20a of the housing 20. The outer peripheral surface of the annular portion 52 and the inner peripheral surface of the trunk portion 20a are tightly joined in an airtight manner over the entire circumference. The fixing member 50 divides the interior of the housing 20 into an upper space 23 for accommodating the compression mechanism 40 and a lower space 24 for accommodating the motor 30.

[0068] A back pressure space 90 is formed between the annular portion 52 of the stationary member 50 and the orbiting-side end plate 71 of the orbiting scroll 70. The back pressure space 90 is a space where back pressure for pressing the orbiting scroll 70 against the fixed scroll 60 acts.

[0069] An annular groove 56 is formed on the upper surface of the annular portion 52 (the surface located on the side of the orbiting scroll 70). The annular groove 56 is formed on the radially outer side of the recessed portion 53. An annular seal ring 57 is accommodated in the annular groove 56. The seal ring 57 is embedded in the annular groove 56 and is held in contact with the back surface of the orbiting side end plate 71 of the orbiting scroll 70.

[0070] The sealing ring 57 seals the gap between the fixed component 50 and the revolving side end plate 71 by abutting against the back surface of the revolving side end plate 71 of the revolving scroll 70. In other words, the sealing ring 57 divides the back pressure space 90 into a first back pressure space 91 formed on the inner peripheral side of the annular groove 56 and a second back pressure space 92 formed on the outer peripheral side of the annular groove 56.

[0071] The first back pressure space 91 is formed by the crank chamber 54. An oil discharge passage (not shown) opened at the bottom of the first back pressure space 91 is formed on the fixed member 50. The oil discharge passage connects the first back pressure space 91 with the lower space 24, and discharges the lubricating oil in the first back pressure space 91 to the lower space 24. The second back pressure space 92 is formed between the upper surface of the annular portion 52 and the back surface of the orbiting scroll 70.

[0072] (2-6) Crosshead coupling

[0073] A cross coupling 45 is provided on the upper portion of the fixing member 50. Figure 2 and Figure 3 As shown in FIG. 1 , the cross coupling 45 is arranged in the second back pressure space 92. The cross coupling 45 prevents the orbiting scroll 70 from rotating on its own. A key 46 is provided on the cross coupling 45. The key 46 faces the back side ( Figure 2 A key groove 47 is formed on the back side of the orbiting side end plate 71 of the orbiting scroll 70. The key 46 of the Oldham coupling 45 is slidably fitted into the key groove 47.

[0074] It should be noted that, although not shown, a key is also provided on the side of the Oldham coupling 45 close to the fixing member 50 , and the key on the side close to the fixing member 50 is slidably fitted into a keyway (not shown) of the fixing member 50 .

[0075] (2-7) Lower bearing

[0076] The lower bearing 22 is an auxiliary bearing member that supports the drive shaft 11 so that it can rotate. The lower bearing 22 is provided at the end portion ( Figure 2 The lower bearing 22 is accommodated in the housing 20. The lower bearing 22 is arranged below the motor 30. The lower bearing 22 is fixed to the inner peripheral surface of the housing 20.

[0077] (2-7) Oil supply line

[0078] An oil supply passage 16 is formed inside the drive shaft 11. The oil supply passage 16 extends from the lower end of the drive shaft 11 to the upper end in the vertical direction. A pump 25 is connected to the lower end of the drive shaft 11. The pump 25 is, for example, a positive displacement pump. The lower end of the pump 25 is immersed in the oil storage portion 21.

[0079] The pump 25 sucks up the lubricating oil from the oil reservoir 21 as the drive shaft 11 rotates, and delivers the lubricating oil to the oil supply passage 16. The oil supply passage 16 supplies the lubricating oil in the oil reservoir 21 to the sliding surface between the lower bearing 22 and the drive shaft 11, and the sliding surface between the upper bearing 51 and the drive shaft 11, and supplies the lubricating oil to the sliding surface between the flange portion 73 and the drive shaft 11. The oil supply passage 16 opens on the upper end surface of the drive shaft 11, and supplies the lubricating oil to the upper side of the drive shaft 11.

[0080] The recessed portion 53 of the fixed member 50 is connected to the oil supply passage 16 of the drive shaft 11 via the interior of the flange portion 73 of the orbiting scroll 70. High-pressure lubricating oil is supplied to the crank chamber 54 formed by the recessed portion 53. As a result, a high pressure equivalent to the discharge pressure of the compression mechanism 40 acts on the crank chamber 54. In other words, the pressure of the first back pressure space 91 is equivalent to the discharge pressure of the compression mechanism 40.

[0081] (2-8) Primary side passage, secondary side passage

[0082] like Figure 4 As shown, a primary passage 48 is formed on the lower surface of the outer peripheral wall 63 of the fixed scroll 60. The radially inner end of the primary passage 48 opens on the inner peripheral surface of the outer peripheral wall 63 and communicates with the compression chamber S in the medium pressure state.

[0083] A secondary passage 49 is formed on the outer periphery of the revolving side end plate 71 of the revolving scroll 70. The secondary passage 49 is composed of a through hole that penetrates the revolving side end plate 71 in the up-down direction. The upper end of the secondary passage 49 is intermittently connected to the radially outer end of the primary passage 48, and the lower end of the secondary passage 49 is connected to the second back pressure space 92 located between the revolving scroll 70 and the fixed component 50. In other words, the intermediate pressure refrigerant is intermittently supplied to the second back pressure space 92 from the compression chamber S in the intermediate pressure state, so that the second back pressure space 92 becomes a predetermined intermediate pressure. The intermediate pressure is higher than the pressure of the fluid (refrigerant) sucked into the compression mechanism 40 and lower than the pressure of the fluid (refrigerant) ejected from the compression mechanism 40.

[0084] (2-9) Oil passage

[0085] An oil passage 55 is formed inside the fixed member 50 and the fixed scroll 60. The inflow end of the oil passage 55 is communicated with the recess 53 of the fixed member 50. The outflow end of the oil passage 55 opens on the opposite surface 66 of the fixed scroll 60. The oil passage 55 supplies the high-pressure lubricating oil in the recess 53 to the opposite surfaces of the orbiting side end plate 71 of the orbiting scroll 70 and the outer peripheral wall 63 of the fixed scroll 60.

[0086] (2-10) Stationary side oil groove and dynamic side oil groove

[0087] like Figure 4 As shown, on the surface ( Figure 2 A stationary side oil groove 80 is formed on the lower side) 66 of the cylinder.

[0088] The stationary oil groove 80 includes a stationary circumferential groove portion 81 and a stationary radial groove portion 82. The stationary circumferential groove portion 81 extends in the circumferential direction along the inner peripheral surface of the outer peripheral wall 63 of the stationary scroll 60. The stationary circumferential groove portion 81 is connected to the oil passage 55. Thus, high-pressure lubricating oil equivalent to the discharge pressure of the compression mechanism 40 is supplied from the oil passage 55 to the stationary circumferential groove portion 81.

[0089] The stationary side radial groove portion 82 extends radially outward and communicates with the stationary side circumferential groove portion 81. In the present embodiment, the stationary side radial groove portion 82 is formed at one end portion ( Figure 4 The fixed scroll 60 has an end portion in the counterclockwise direction. The fixed scroll 60 has an end portion in the counterclockwise direction. The fixed scroll 60 has an end portion in the counterclockwise direction. The fixed scroll 60 has an end portion in the counterclockwise direction.

[0090] In the present embodiment, the stationary radial groove portion 82 is connected to the end portion of the stationary circumferential groove portion 81 located on the front side in the rotation direction of the orbiting scroll 70. In addition, the stationary radial groove portion 82 is connected to the end portion of the stationary circumferential groove portion 81 close to the suction port 64. By forming the stationary radial groove portion 82 at one end portion of the stationary circumferential groove portion 81, lubricating oil can be sufficiently supplied to one end portion of the stationary circumferential groove portion 81.

[0091] When the orbiting scroll 70 tilts and tilts greatly, the stationary radial groove 82 communicates with the second back pressure space 92. Specifically, if the orbiting scroll 70 tilts, a large gap is formed in a portion between the orbiting scroll 70 and the stationary scroll 60. In the portion with a large gap, the sealing function achieved by the lubricating oil disappears. As a result, the stationary radial groove 82 communicates with the second back pressure space 92.

[0092] It should be noted that the stationary radial groove portion 82 may also be formed in the middle portion of the stationary circumferential groove portion 81 except for the end portion. The stationary oil groove 80 corresponds to the oil groove of the present disclosure. The stationary circumferential groove portion 81 corresponds to the circumferential groove portion of the present disclosure. The stationary radial groove portion 82 corresponds to the circumferential groove portion of the present disclosure.

[0093] like Figure 4 As shown, an orbiting side oil groove 85 is formed on the surface of the orbiting scroll 70 that faces the fixed scroll 60. The orbiting side oil groove 85 includes an orbiting side circumferential groove portion 86 and an orbiting side radial groove portion 87. The orbiting side circumferential groove portion 86 extends along the outer peripheral surface of the orbiting side wrap 72 in the circumferential direction.

[0094] The rotating side radial groove portion 87 extends in the radial direction and is connected to one end portion ( Figure 4 The revolving side radial groove portion 87 is connected to the fluid chamber F at the end portion in the counterclockwise direction of the revolving side circumferential groove portion 86. The revolving side radial groove portion 87 extends in a manner that bends from one end portion of the revolving side circumferential groove portion 86 toward the center side of the revolving scroll 70. In other words, the revolving side radial groove portion 87 extends radially inward on the revolving side end plate 71 of the revolving scroll 70. Furthermore, the radially inner end portion of the revolving side radial groove portion 87 can be connected to the fluid chamber F.

[0095] As the orbiting scroll 70 rotates eccentrically, the communication state between the inner end of the orbiting radial groove 87 and the stationary oil groove 80 and the fluid chamber F is switched. As a result, the high-pressure lubricating oil in the stationary oil groove 80 is supplied to the compression chamber S, the opposing surfaces of the stationary scroll 60 and the orbiting scroll 70, the key groove 47, etc.

[0096] like Figure 4 As shown, on the opposite surface 66 of the fixed scroll 60 and the orbiting scroll 70, the length from the outer end of the fixed side radial groove portion (the radially outer end) to the outer edge of the orbiting scroll 70, that is, the sealing length L1 is 2 mm or more. In the present embodiment, the sealing length L1 is 2 mm. Thus, when the orbiting scroll 70 is operating stably (when the orbiting scroll 70 is not tilted), it is possible to suppress leakage of high-pressure lubricating oil from the fixed side oil groove 80.

[0097] (3) Operation

[0098] The operation of the scroll compressor 10 will be described.

[0099] exist Figure 2 In the embodiment, when the motor 30 is operated, the drive shaft 11 is driven to rotate. The orbiting scroll 70 orbits along with the rotation of the drive shaft 11. Here, since the orbiting scroll 70 is prevented from rotating by the Oldham coupling 45, the orbiting scroll 70 rotates eccentrically around the axis of the drive shaft 11.

[0100] When the orbiting scroll 70 orbits, the gaseous refrigerant flowing into the suction port 64 through the suction pipe 12 is compressed in the compression chamber S. Specifically, when the orbiting scroll 70 orbits, the gaseous refrigerant is gradually sucked into the fluid chamber F on the outermost peripheral side from the suction port 64, and then the fluid chamber F is closed to divide the compression chamber S. When the drive shaft 11 further rotates, the volume of the compression chamber S on the outermost peripheral side is reduced, and the compression chamber S gradually approaches the discharge port 65 side.

[0101] At this time, the drive shaft 11 rotates to rotate the orbiting scroll 70, and the primary passage 48 and the secondary passage 49 are connected with each other. As a result, the gaseous refrigerant in the compression process in the compression chamber S passes through the primary passage 48 and the secondary passage 49 in sequence, and begins to be introduced into the second back pressure space 92. If the orbiting scroll 70 further rotates from this state, the opening area of ​​the primary passage 48 relative to the opening of the secondary passage 49 reaches the maximum. As a result, the second back pressure space 92 is maintained at a predetermined target pressure, and a predetermined thrust force acts on the back of the orbiting side end plate 71 of the orbiting scroll 70. The thrust force here refers to the force that pushes up the back of the orbiting scroll 70 and pushes the orbiting scroll 70 against the fixed scroll 60. If the orbiting scroll 70 further rotates from this state, the primary passage 48 and the secondary passage 49 are disconnected from each other, and the introduction of the gaseous refrigerant into the second back pressure space 92 ends.

[0102] Then, if the drive shaft 11 rotates and the revolving scroll 70 further revolves, the compression chamber S near the center is connected to the discharge port 65. The high-pressure gas refrigerant compressed in the compression chamber S is discharged from the discharge port 65 and flows into the upper space 23 of the shell 20. The gas refrigerant in the upper space 23 flows out to the lower space 24 through the discharge passage (not shown) formed in the fixed member 50. The high-pressure gas refrigerant in the lower space 24 is discharged to the outside of the shell 20 through the discharge pipe 13.

[0103] (4) Oil supply action

[0104] Next, the operation of supplying lubricating oil to the scroll compressor (10) will be described.

[0105] As the drive shaft 11 rotates, the high-pressure lubricating oil in the oil reservoir 21 is sucked up by the pump 25 and flows upward in the oil supply passage 16 of the drive shaft 11 , and flows out from the upper end opening of the eccentric portion 15 of the drive shaft 11 into the interior of the flange portion 73 of the orbiting scroll 70 .

[0106] The lubricating oil supplied to the flange portion 73 flows out to the recessed portion 53 of the fixed member 50 through the gap between the eccentric portion 15 of the drive shaft 11 and the flange portion 73. As a result, the pressure of the crank chamber 54 (first back pressure space 91) of the fixed member 50 reaches a high pressure equivalent to the discharge pressure of the compression mechanism 40. Under the action of the high pressure in the first back pressure space 91 and the medium pressure in the second back pressure space 92, the orbiting scroll 70 is pushed toward the fixed scroll 60.

[0107] The high-pressure lubricating oil accumulated in the recess 53 flows out to the stationary oil groove 80 via the oil passage 55. The lubricating oil flowing in from the oil passage 55 flows circumferentially to both ends in the stationary circumferential groove 81, and then flows into the stationary radial groove 82 at one end. The lubricating oil flowing into the stationary radial groove 82 flows radially outward. Thus, high-pressure lubricating oil equivalent to the discharge pressure of the compression mechanism 40 is supplied to the stationary oil groove 80. The high-pressure lubricating oil flowing into the stationary oil groove 80 is supplied to the sliding surface between the stationary scroll 60 and the orbiting scroll 70, and then returns to the oil storage portion 21.

[0108] Here, in the normal state when the scroll compressor 10 is in operation, due to the internal pressure of the compression chamber S, a separation force (a force separating each other) that separates the orbiting scroll 70 from the fixed scroll 60 acts on the orbiting scroll 70. On the other hand, the orbiting scroll 70 is pushed toward the fixed scroll 60 side by the high pressure in the first back pressure space 91 and the medium pressure in the second back pressure space 92. In this way, in the normal state of the scroll compressor 10, the separation force and the pushing force acting on the orbiting scroll 70 are balanced with each other, thereby stabilizing the movement of the orbiting scroll 70. In the state where the movement of the orbiting scroll 70 is stable, the gap between the orbiting scroll 70 and the fixed scroll 60 is in a substantially uniform state, ensuring the airtightness of the compression chamber S.

[0109] However, due to various factors such as the pressure state of the compression chamber S and the centrifugal force acting on the orbiting scroll 70, the balance between the separation force and the thrust force acting on the orbiting scroll 70 may be disrupted, and the orbiting scroll 70 may exhibit unstable behavior. In the case of such unstable behavior, the orbiting scroll 70 may tilt and become partially separated from the fixed scroll 60 (so-called tilted state).

[0110] As described above, the situation in which the orbiting scroll 70 exhibits unstable behavior is, for example, the situation in which the pressure state of the compression chamber S changes. If the pressure state of the compression chamber S changes, the separation force acting on the orbiting scroll 70 will be different in multiple areas on the orbiting side end plate 71. As a result, the balance between the separation force and the thrust force acting on the orbiting scroll 70 is partially destroyed. In this case, the orbiting scroll 70 tilts, thereby forming a relatively narrow portion and a relatively wide portion in the gap between the orbiting scroll 70 and the fixed scroll 60.

[0111] In the present embodiment, since high-pressure lubricating oil is supplied to the stationary radial groove portion 82, when the orbiting scroll 70 begins to tilt, a separation force acts on the narrower part of the above-mentioned gap due to the high pressure in the stationary radial groove portion 82. At this time, since the stationary radial groove portion 82 extends radially outward, the high pressure acts on a position far from the center of gravity of the orbiting scroll 70. As a result, the torque that pulls the stationary scroll 60 away from the orbiting scroll 70 can be increased, and the gap between the orbiting scroll 70 and the stationary scroll 60 can be maintained in a uniform state. As a result, the movement of the orbiting scroll 70 can be maintained in a stable state, and the tilting state of the orbiting scroll 70 can be suppressed.

[0112] In addition, when the pressure of the refrigerant introduced into the second back pressure space 92 becomes lower than the predetermined target pressure, the pushing force acting on the orbiting scroll 70 becomes relatively small (insufficient) relative to the separation force. As a result, the balance between the separation force and the pushing force acting on the orbiting scroll 70 is destroyed. Therefore, the movement of the orbiting scroll 70 becomes unstable, and the orbiting scroll 70 may tilt.

[0113] In contrast, in the present embodiment, when the orbiting scroll 70 tilts and inclines, since the stationary radial groove portion 82 is connected to the second back pressure space 92, the high-pressure lubricating oil is supplied from the outer end of the stationary radial groove portion 82 to the second back pressure space 92. As a result, the pressure in the second back pressure space 92 rises, and the thrust acting on the back of the orbiting scroll 70 increases. As a result, the orbiting scroll 70 can be restored from the tilted state as soon as possible. In addition, at this time, along with the orbiting motion of the orbiting scroll 70, the lubricating oil between the respective opposing surfaces (sliding surfaces) of the orbiting scroll 70 and the stationary scroll 60 is scraped out and supplied to the second back pressure space 92. As a result, the high-pressure lubricating oil is supplied to the second back pressure space 92, so the thrust acting on the back of the orbiting scroll 70 increases, and the orbiting scroll 70 can be restored from the tilted state as soon as possible.

[0114] (5) Measurement of the movement of the orbiting scroll

[0115] Below, refer to Figure 5 and Figure 6 The operation measurement of the orbiting scroll 70 will be described.

[0116] In this measurement, the movement of the orbiting scroll 70 during operation of a conventional scroll compressor 10 in which the stationary radial groove portion 82 of the present embodiment is not formed is measured. Specifically, the displacement of the orbiting scroll 70 is measured by installing a plurality of distance sensors on the outer peripheral wall 63 of the stationary scroll 60 of the compression mechanism 40. In other words, in this measurement, the gap size (displacement) between the stationary scroll 60 and the orbiting scroll 70 at each sensor position is measured during the operation of the scroll compressor 10.

[0117] In this measurement, Figure 5 The distance sensors are arranged at the three positions shown in Figure 1, point A, point B, and point C. The measurement results at each sensor position are shown in Figure 1. Figure 6 In. Figure 6 In the figure, the measurement result at point A is represented by a solid line, the measurement result at point B is represented by a dashed line, and the measurement result at point C is represented by a dotted line.

[0118] Focus on Figure 6 The middle crankshaft angle is in the range of 135 degrees to 220 degrees. In this range, the displacement decreases sharply at point A and increases sharply at point B. It can be seen that the orbiting scroll 70 in this range is rapidly approaching the fixed scroll 60 near point A and rapidly moving away from the fixed scroll 60 near point B.

[0119] It can be considered that: since the refrigerant gas is ejected from the compression chamber S when the crankshaft angle is near 114 degrees, the pressure relationship in the compression chamber S changes with the ejection. Due to this change, when the crankshaft angle is near 135 degrees, the balance of the separation force acting on the orbiting scroll 70 at points A and B is destroyed, so that the gap size at each position changes (in other words, the tilting mode of the orbiting scroll 70 changes). It can be seen that: when the crankshaft angle is near 135 degrees, it is the starting time for the orbiting scroll 70 to start tilting. At this time, near point A, the orbiting scroll 70 is approaching the fixed scroll 60.

[0120] And, from Figure 6 Starting from the crankshaft angle of 220 degrees, the displacement slowly increases at point A and slowly decreases at point B. Then, the displacement fluctuation ranges of point A and point B become smaller. It can be seen that after the crankshaft angle exceeds 220 degrees, the orbiting scroll 70 recovers from the tilted state.

[0121] In the present embodiment, based on the measurement results of the movement of the above-mentioned orbiting scroll 70, a stationary radial groove portion 82 extending radially outward is provided near point A on the fixed scroll 60. By providing the stationary radial groove portion 82 at a position close to point A on the fixed scroll 60, high pressure acts on a position far from the center of gravity of the orbiting scroll 70. Thus, at the moment when the orbiting scroll 70 begins to tilt, the torque that pulls the fixed scroll 60 away from the orbiting scroll 70 can be increased, and the orbiting scroll 70 can be restrained from approaching the fixed scroll 60. Thus, the tilting movement of the orbiting scroll 70 can be reduced, and the gap between the orbiting scroll 70 and the fixed scroll 60 can be maintained in a uniform state. As a result, the tilting state of the orbiting scroll 70 can be suppressed.

[0122] (6) Edge collapse limit test

[0123] Below, refer to Figure 7 The edge collapse limit test will be described.

[0124] In the collapse limit test, the revolving scroll 70 is intentionally placed in a tilted state by causing the pressure in the second back-pressure space 92 to reach a low pressure (a pressure equivalent to the suction pressure of the compression mechanism 40), and then the revolving scroll 70 is restored from the tilted state by adjusting the high pressure in such a way as to reduce the difference between the low pressure and the high pressure of the compression mechanism 40. Figure 7 The graph is a graph recording the ratio Pr (Hp / Lp) of the high pressure Hp to the low pressure Lp when the orbiting scroll 70 recovers from the tilting state at each rotation speed.

[0125] It should be noted that in Figure 7 , the test results of the conventional scroll compressor 10 in which the stationary-side radial groove portion 82 is not formed are indicated by circular marks, and the test results of the scroll compressor 10 of the present embodiment in which the stationary-side radial groove portion 82 is formed are indicated by triangular marks.

[0126] like Figure 7 As shown, at a rotation speed of 20 rps or more, the Pr value of the scroll compressor 10 of the present embodiment is smaller than the Pr value of the conventional scroll compressor 10. This means that the scroll compressor 10 of the present embodiment recovers from the tilted state with a smaller difference between the high pressure and the low pressure than the conventional scroll compressor 10. It can be confirmed that the scroll compressor 10 of the present embodiment can recover from the tilted state earlier than the conventional scroll compressor 10.

[0127] (7) Features

[0128] (7-1) Feature 1

[0129] The stationary oil groove (80) includes a stationary radial groove portion (82) extending radially outward from the stationary scroll (60) and communicating with the stationary circumferential groove portion (81).

[0130] Therefore, when the orbiting scroll 70 begins to tilt, due to the pressure in the stationary side radial groove portion 82 supplied with high-pressure lubricating oil, a force that pulls the orbiting scroll 70 away from the stationary scroll 60 acts in the narrower portion of the gap between the orbiting scroll 70 and the stationary scroll 60. At this time, since the stationary side radial groove portion 82 extends radially outward of the stationary scroll 60, high pressure acts on a position far from the center of gravity of the orbiting scroll 70. As a result, the torque that pulls the orbiting scroll 70 away from the stationary scroll 60 can be increased, and the gap between the orbiting scroll 70 and the stationary scroll 60 can be maintained in a uniform state. As a result, the movement of the orbiting scroll 70 can be maintained in a stable state, and the tilting state of the orbiting scroll 70 can be suppressed.

[0131] (7-2) Feature 2

[0132] When the orbiting scroll (70) tilts, the stationary radial groove (82) communicates with the second back pressure space (92).

[0133] Therefore, when the orbiting scroll 70 tilts, high-pressure lubricating oil is supplied from the end of the stationary radial groove 82 to the second back pressure space 92. As a result, the pressure in the second back pressure space 92 rises, and the force that pushes up the back side of the orbiting scroll 70 and presses the orbiting scroll 70 against the stationary scroll 60 increases. As a result, the orbiting scroll 70 can be restored from the tilted state as soon as possible.

[0134] (7-3) Feature 3

[0135] The stationary-side radial groove portion 82 is formed at the end portion of the stationary-side circumferential groove portion 81. Therefore, the lubricating oil can be sufficiently supplied to the end portion of the stationary-side circumferential groove portion 81.

[0136] (7-4) Feature 4

[0137] A seal length L1 , which is a length from the end of the radial groove portion 82 to the outer edge of the orbiting scroll 70 on the facing surface 66 of the fixed scroll 60 , is 2 mm or more.

[0138] Therefore, in a state where the orbiting scroll (70) operates stably, leakage of the high-pressure lubricating oil from the oil groove (80) can be suppressed.

[0139] (7-5) Feature 5

[0140] The refrigeration device 1 includes a scroll compressor 10 according to the present embodiment and a refrigerant circuit 1 a through which the refrigerant compressed by the scroll compressor 10 flows.

[0141] Therefore, it is possible to provide a refrigeration device 1 including the scroll compressor 10 in which the orbiting scroll 70 is prevented from being tilted.

[0142] The above embodiments and variations are described, but it should be understood that various changes can be made to the methods and specific circumstances without departing from the spirit and scope of the claims. In addition, the above embodiments, variations, and other embodiments may be appropriately combined or replaced.

[0143] The terms "first", "second", etc. mentioned above are only used to distinguish the sentences containing the above terms, and are not intended to limit the number or order of the sentences.

[0144] - Industrial Applicability -

[0145] In summary, the present disclosure is very useful for scroll compressors and refrigeration devices.

[0146] - Explanation of symbols -

[0147] 1 Refrigeration unit

[0148] 1a Refrigerant circuit

[0149] 10 Scroll compressor

[0150] 20 Shell

[0151] 40 Compression mechanism

[0152] 50 Fixed parts

[0153] 56 Ring groove

[0154] 57 Sealing ring

[0155] 60 static scroll

[0156] 61 Static side end plate

[0157] 62 Stationary scroll

[0158] 63 Outer wall

[0159] 66 Opposite side

[0160] 70 Orbital Scroll

[0161] 71 Swing side end plate

[0162] 72 Rotating scroll

[0163] 80 static side oil tank (oil tank)

[0164] 81 static side circumferential groove (circumferential groove)

[0165] 82 radial groove on the stationary side (radial groove)

[0166] 90 Backpressure Space

[0167] 91 First back pressure space

[0168] 92 Second back pressure space

[0169] L1 Sealing length

Claims

1. A scroll compressor, characterized in that: The scroll compressor comprises a housing (20) and a compression mechanism (40). The compression mechanism (40) is accommodated in the casing (20) and includes a fixed scroll (60) and an orbiting scroll (70). The fixed scroll (60) comprises a fixed side end plate (61), an outer peripheral wall (63) and a fixed side scroll (62), wherein the outer peripheral wall (63) is arranged at the outer edge of the fixed side end plate (61), and the fixed side scroll (62) is spiral-shaped and arranged on the inner side of the outer peripheral wall (63). The revolving scroll (70) comprises a revolving side end plate (71) and a revolving side scroll (72), the front ends of the stationary side end plate (61) and the outer peripheral wall (63) are in sliding contact with the revolving side end plate (71), the revolving side scroll (72) is in a spiral shape, and the revolving side scroll (72) is arranged on the front surface of the revolving side end plate (71) and meshes with the stationary side scroll (62). An oil groove (80) is formed on the opposite surface (66) of the outer peripheral wall (63) to the front surface of the rotary side end plate (71), and high-pressure lubricating oil is supplied to the oil groove (80), the high pressure corresponding to the discharge pressure of the compression mechanism (40). The oil groove (80) comprises a circumferential groove portion (81) and a radial groove portion (82). The circumferential groove (81) extends along the circumference of the fixed scroll (60). The radial groove portion (82) extends radially outward of the fixed scroll (60) and communicates with the circumferential groove portion (81).

2. The scroll compressor according to claim 1, characterized in that: The scroll compressor further comprises a fixing component (50) and a sealing ring (57). The fixed component (50) is arranged on the back side of the orbiting scroll (70), a back pressure space (90) is formed between the fixed component (50) and the orbiting scroll (70), and an annular ring groove (56) is formed on the surface of the fixed component (50) located on the orbiting scroll (70) side. The sealing ring (57) is received in the annular groove (56), and the sealing ring (57) abuts against the back surface of the orbiting scroll (70), thereby dividing the back pressure space (90) into a first back pressure space (91) formed on the inner peripheral side of the annular groove (56) and a second back pressure space (92) formed on the outer peripheral side of the annular groove (56). The pressure in the first back pressure space (91) corresponds to the discharge pressure of the compression mechanism (40). The pressure in the second back pressure space (92) is higher than the pressure of the fluid sucked into the compression mechanism (40) and lower than the pressure of the fluid discharged from the compression mechanism (40). When the orbiting scroll (70) is tilted, the radial groove portion (82) communicates with the second back pressure space (92).

3. The scroll compressor according to claim 1 or 2, characterized in that: The radial groove portion (82) is formed at an end portion of the circumferential groove portion (81).

4. The scroll compressor according to any one of claims 1 to 3, characterized in that: A seal length (L1) is 2 mm or more, and the seal length (L1) is a length from an end of the radial groove portion (82) to an outer edge of the orbiting scroll (70) on the opposing surface (66).

5. A refrigeration device, characterized in that: The refrigeration device comprises: The scroll compressor (10) according to any one of claims 1 to 4; and A refrigerant circuit (1a) through which the refrigerant compressed by the scroll compressor (10) flows.

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