Thrust bearing mechanism

Abstract

Provided is a thrust support mechanism in which a fluid in a high-pressure space is less likely to leak to a low-pressure space side. A thrust support mechanism (8) capable of generating dynamic pressure on the back surface of a movable scroll (42) provided on the back surface of the movable scroll (42) that slides in conjunction with eccentric rotation with respect to a fixed scroll (41), the thrust support mechanism (8) having a dynamic pressure generation unit (81) including a first groove (85) communicating with a low-pressure side (20) and a second groove (86) communicating with the first groove (85), the first groove (85) communicating with a low-pressure side (20), and the second groove (86) communicating with the second groove (86). The second groove (86) communicates with a cushion space between the inner diameter end and the outer diameter end of the thrust support mechanism (8).

Description

Technical Field

[0001] The present invention relates to a thrust bearing mechanism, for example, a thrust bearing mechanism for a rotary machine including an eccentric mechanism. Background Art

[0002] The machines driven by rotation used in various industrial fields include not only the rotating machines whose central shaft rotates while being kept at a fixed position, but also the rotating machines whose central shaft rotates eccentrically. As one of the rotating machines rotating eccentrically, there is a scroll compressor, etc. This compressor is a mechanism as follows: it includes a scroll compression mechanism and an eccentric mechanism that causes the rotating shaft to rotate eccentrically, and the scroll compression mechanism is composed of a fixed scroll having a spiral vortex on the surface of an end plate, and a movable scroll having a spiral vortex on the surface of the end plate. The movable scroll slides relative to the fixed scroll while rotating eccentrically by the rotation of the rotating shaft, thereby pressurizing the fluid supplied from the low-pressure chamber on the outer diameter side of the two scrolls, so that the high-pressure fluid is ejected from the ejection hole formed in the center of the fixed scroll.

[0003] These scroll compressors utilize a mechanism that causes a movable scroll to slide relative to a fixed scroll while rotating eccentrically. This mechanism not only has high compression efficiency but also low noise. Therefore, they are used in many aspects such as refrigeration cycles. However, there is a problem of increased refrigerant leakage from the axial gap between the two scrolls.

[0004] The scroll compressor shown in Patent Document 1 is provided with a thrust bearing on the back side of a movable scroll disk, and an annular plate is provided on the thrust bearing. A plurality of spiral groove mechanisms are independently formed along the circumferential direction on the surface of the movable scroll disk side of the annular plate. Each spiral groove mechanism is provided with a plurality of grooves in a substantially radial manner toward the central table surface of the spiral mechanism. In detail, each groove extends radially while tilting in the counterclockwise direction from the central table surface, and the front end of one end on the table surface side becomes thinner, and the other end on the opposite side of the table surface is wider than the one end.

[0005] The movable scroll moves from the other end of the groove to one end when rotating eccentrically. As a result, the fluid on the outer diameter side or inner diameter side of the annular plate is introduced into the groove, generating dynamic pressure near one end of the groove. As a result, the movable scroll and the sliding surface of the annular plate can float and form a fluid film to improve the sliding performance, and the movable scroll can be pressed against the fixed scroll to reduce the leakage of refrigerant from the axial gap between the two scrolls. Prior art literature Patent Literature

[0006] Patent Document 1: Japanese Patent Application Laid-Open No. 9-317666 (page 4, Figure 4 ) Summary of the invention Problems to be solved by the invention

[0007] However, in the scroll compressor of Patent Document 1, the groove arranged on the low-pressure side of the spiral groove mechanism sucks the fluid in the low-pressure chamber and generates dynamic pressure toward the high-pressure chamber side, pushing the fluid back, but the groove arranged on the high-pressure side of the spiral groove mechanism sucks the fluid in the high-pressure chamber and generates dynamic pressure toward the low-pressure chamber side. Therefore, the fluid in the high-pressure chamber that originally tends to flow toward the low-pressure side may flow in large quantities to the low-pressure chamber side from between the sliding surface of the movable scroll disk and the annular plate.

[0008] The present invention has been made in view of such a problem, and an object of the present invention is to provide a thrust support mechanism in which fluid in a high-pressure space is unlikely to leak to a low-pressure space side. Means of solving problems

[0009] In order to solve the above problems, the thrust support mechanism of the present invention is provided on the back side of the movable scroll that slides relatively with the fixed scroll as it rotates eccentrically, and can generate dynamic pressure on the back side of the movable scroll. The thrust support mechanism has a dynamic pressure generating portion including a first groove communicating with the low pressure side and a second groove communicating with a buffer space between an inner diameter end and an outer diameter end of the thrust support mechanism. Thus, each groove guides the fluid on the low-pressure side to the high-pressure side, making it difficult for the fluid on the high-pressure side outside the sliding surface to enter between the sliding surfaces. Therefore, it is possible to suppress the fluid on the high-pressure side from leaking to the low-pressure side. In addition, the fluid flowing out from the first groove to between the sliding surfaces can be stored in the buffer space, and the fluid can be supplied from the buffer space to the second groove.

[0010] The buffer space may be a recess. Thus, the fluid passing through the buffer space can more reliably generate dynamic pressure in the second groove without being affected by the axial positions of the thrust support mechanism and the movable scroll.

[0011] The recess may be in communication with the low-pressure side. This prevents the fluid in the recess from drying up, and enables stable sliding properties to be exhibited.

[0012] In the thrust support mechanism, the dynamic pressure generating portions having a smaller diameter than the diameter of the thrust support mechanism are evenly arranged at intervals in a circumferential direction of the thrust support mechanism. This can suppress leakage of the fluid on the high-pressure side to the low-pressure side throughout the circumferential direction. BRIEF DESCRIPTION OF THE DRAWINGS

[0013] Figure 1 This is a schematic structural diagram showing a scroll compressor to which a thrust plate as a thrust support mechanism according to the first embodiment of the present invention is applied. Figure 2It is a schematic diagram showing the sliding surface of the thrust plate in Example 1 of the present invention. Figure 3 The figures show the relative sliding between the sliding surface of the side seal and the sliding surface of the thrust plate in Example 1 of the present invention. It should be noted that (a) is the starting position, (b) shows the relative sliding position between the sliding surface of the side seal and the sliding surface of the thrust plate when the rotating shaft is eccentrically rotated to 90 degrees, (c) shows the relative sliding position between the sliding surface of the side seal and the sliding surface of the thrust plate when the rotating shaft is eccentrically rotated to 270 degrees. Figure 4 Yes means Figure 3 Schematic diagram of the sliding state of a dynamic pressure generating portion and a side seal in the state of (a). Figure 5 Yes means Figure 3 Schematic diagram of the sliding state of a dynamic pressure generating portion and a side seal in the state (c). Figure 6 It is a schematic diagram showing a thrust plate according to a second embodiment of the present invention. DETAILED DESCRIPTION

[0014] Next, a mode for implementing the thrust support mechanism of the present invention will be described based on an embodiment. Example 1

[0015] Reference Figures 1 to 5 The thrust support mechanism of the first embodiment will be described.

[0016] The thrust support mechanism of the present invention is applicable to a rotary machine including an eccentric mechanism, for example, a scroll compressor C used in an air conditioning system of an automobile, etc., which sucks, compresses, and ejects a refrigerant as a fluid. It should be noted that in this embodiment, the refrigerant is a gas mixed with mist-like lubricating oil.

[0017] First, the scroll compressor C will be described. Figure 1 As shown, the scroll compressor C is mainly composed of a housing 1, a rotating shaft 2, an inner casing 3, a scroll compression mechanism 4, a side seal 7, a thrust plate 8 as a thrust support mechanism, and a drive motor M.

[0018] The housing 1 is composed of a cylindrical outer shell 11 and a cover 12 that closes an opening of the outer shell 11. The opening of the outer shell 11 on the axially opposite side to the opening closed by the cover 12 is closed by the drive motor M.

[0019] A low-pressure chamber 20, a high-pressure chamber 30, and a back-pressure chamber 50 are formed inside the shell 11. A low-pressure refrigerant is supplied from a refrigerant circuit (not shown) through a suction port 10 to the low-pressure chamber 20 as an external space on the low-pressure side; a high-pressure refrigerant compressed by the scroll compression mechanism 4 is ejected from the high-pressure chamber 30; and a lubricating oil and a portion of the refrigerant compressed by the scroll compression mechanism 4 are supplied to the back-pressure chamber 50 as an external space on the high-pressure side. It should be noted that the back-pressure chamber 50 is formed inside the cylindrical inner shell 3, and the inner shell 3 is accommodated inside the shell 11.

[0020] The cover 12 is provided with a discharge communication passage 13 that connects a refrigerant circuit (not shown) and the high-pressure chamber 30. In addition, the cover 12 is provided with a portion of a back-pressure communication passage 14 that connects the high-pressure chamber 30 and the back-pressure chamber 50 so as to branch from the discharge communication passage 13. It should be noted that the discharge communication passage 13 is provided with an oil separator 6 that separates lubricating oil from refrigerant.

[0021] The inner shell 3 is fixed in a state where its axial end portion abuts against the end plate 41a of the fixed scroll 41 constituting the scroll compression mechanism 4. In addition, a suction communication passage 15 penetrating in the radial direction is formed on the side wall of the inner shell 3. That is, the low-pressure chamber 20 is formed from the outside of the inner shell 3 to the inside of the inner shell 3 via the suction communication passage 15. The refrigerant supplied to the inside of the inner shell 3 through the suction communication passage 15 is sucked into the scroll compression mechanism 4.

[0022] The scroll compression mechanism 4 is mainly composed of a fixed scroll 41 fixed in a sealed manner to the cover 12 , and a movable scroll 42 accommodated in the inner casing 3 .

[0023] The fixed scroll 41 is made of metal and includes a spiral volute 41b protruding from the surface of a circular plate-shaped end plate 41a, that is, the end plate 41a toward the movable scroll 42. In addition, a recessed portion 41c is formed on the fixed scroll 41, which is recessed in the direction opposite to the cover 12 on the inner diameter side of the end surface of the end plate 41a that abuts against the cover 12, and the high-pressure chamber 30 is divided by the recessed portion 41c and the cover 12.

[0024] The movable scroll 42 is made of metal and includes a spiral volute 42b protruding from the surface of a circular plate-shaped end plate 42a, that is, the end plate 42a toward the fixed scroll 41. In addition, a boss 42c protruding from the center of the back side of the end plate 42a is formed on the movable scroll 42. The eccentric portion 2a formed on the rotating shaft 2 is inserted into the boss 42c in a relatively rotatable manner. It should be noted that in the present embodiment, the eccentric portion 2a of the rotating shaft 2 and the counterweight portion 2b protruding from the rotating shaft 2 in the outer diameter direction constitute an eccentric mechanism for causing the rotating shaft 2 to rotate eccentrically.

[0025] When the rotating shaft 2 is driven to rotate by the driving motor M, the eccentric portion 2a rotates eccentrically, and the movable scroll 42 slides relative to the fixed scroll 41 while maintaining its posture and eccentrically rotating. At this time, the movable scroll 42 rotates eccentrically relative to the fixed scroll 41, and with this rotation, the contact positions of the volutes 41b and 42b move in sequence along the rotation direction, and the compression chamber 40 formed between the volutes 41b and 42b gradually shrinks while moving toward the center. As a result, the refrigerant sucked into the compression chamber 40 from the low-pressure chamber 20 formed on the outer diameter side of the scroll compression mechanism 4 is compressed, and finally the high-pressure refrigerant is ejected to the high-pressure chamber 30 through the ejection hole 41d provided in the center of the fixed scroll 41.

[0026] Next, the side seal 7 will be described. The side seal 7 is made of resin, has a rectangular cross-section and a circular ring shape when viewed in the axial direction, and is fixed to the back surface of the end plate 42 a of the movable scroll 42 .

[0027] The side seal 7 has a sliding surface 8a (see Figure 1 ) abuts against the sliding surface 7a. The sliding surface 7a is a flat surface and constitutes the back side sliding surface of the movable scroll 42.

[0028] Next, the thrust plate 8 will be described. Figure 1 and Figure 2 As shown, the thrust plate 8 is made of metal and has a circular ring shape. The thrust plate 8 is composed of a plurality of dynamic pressure generating portions 81 (16 in this embodiment) and a plurality of connecting portions 82 (16 in this embodiment).

[0029] The dynamic pressure generating parts 81 adjacent to each other in the circumferential direction are connected by the connecting part 82. The connecting part 82 has the same thickness as the base part 83 of the dynamic pressure generating part 81, and has a smaller radial width than the base part 83. That is, the dynamic pressure generating part 81 bulges further toward the inner diameter side and the outer diameter side of the thrust plate 8 than the connecting part 82. In other words, when viewed from the axial direction, the dynamic pressure generating part 81 and the connecting part 82 are respectively formed with step portions on the inner diameter side and the outer diameter side. Hereinafter, these step portions are simply recorded as "step portions of the dynamic pressure generating part 81 and the connecting part 82".

[0030] The dynamic pressure generating portion 81 includes a base 83, a recessed portion 84 as a buffer space, a first inclined groove group 85 as a first groove, and a second inclined groove group 86 as a second groove. It should be noted that the recessed portion 84, the first inclined groove group 85, and the second inclined groove group 86 are relatively small in size, so Figure 1 In order to facilitate the explanation, their illustrations are omitted. In addition, in order to easily understand that the concave portion 84 is a bottomed hole, Figure 2 In the enlarged portion of FIG. 1 , a dot is marked on the recess 84 for convenience of explanation.

[0031] The base portion 83 has a circular shape when viewed in the axial direction.

[0032] The recessed portion 84 is formed at the center of the base portion 83, that is, between the inner diameter end and the outer diameter end of the thrust plate 8, and is open toward the sliding surface 8a. The recessed portion 84 is a bottomed recessed portion that is circular in shape when viewed in the axial direction.

[0033] The first inclined groove group 85 is provided on the sliding surface 8a side of the base 83 at a position closer to the low pressure chamber 20 than the recessed portion 84. The first inclined groove group 85 is composed of a plurality of first inclined grooves 851 (eight in this embodiment).

[0034] The first inclined groove 851 extends from one end 851a on the low pressure chamber 20 side toward the other end 851b on the back pressure chamber 50 side along one side in the circumferential direction (in this embodiment, Figure 2 One end 851a is connected to the low pressure chamber 20, and the other end 851b is a closed end. In other words, the other end 851b of the first inclined groove 851 is separated from the recess 84 by the table surface.

[0035] The second inclined groove group 86 is provided on the sliding surface 8a side of the base 83 at a position closer to the back pressure chamber 50 than the recessed portion 84. The second inclined groove group 86 is composed of a plurality of second inclined grooves 861 (eight in this embodiment).

[0036] The second inclined groove 861 extends from one end 861a on the low pressure chamber 20 side toward the other end 861b on the back pressure chamber 50 side along one side in the circumferential direction (in this embodiment, Figure 2 The second inclined groove 861 extends while being inclined (in the counterclockwise direction in FIG. 1 ). One end 861a is connected to the recess 84, and the other end 861b is a closed end. In other words, the other end 861b of the second inclined groove 861 is separated from the back pressure chamber 50 and the second inclined groove 861 by the table surface. That is, each second inclined groove 861 is not connected to the back pressure chamber 50.

[0037] The thrust plate 8 is fitted into the installation groove 3b provided in the inner shell 3. The inner wall constituting the installation groove 3b has a substantially similar shape slightly larger than the outer shape of the thrust plate 8, and the step portion of the dynamic pressure generating portion 81 and the connecting portion 82 is engaged with the inner wall, thereby restricting the circumferential rotation of the thrust plate 8.

[0038] In addition, a seal ring 43 is fixed to the back side of the thrust plate 8 (see Figure 1 The seal ring 43 contacts the bottom surface of the installation groove 3b of the inner casing 3. Thus, the thrust plate 8 functions as a thrust support mechanism that receives the axial load of the movable scroll 42 via the side seal 7.

[0039] In addition, the side seal 7 and the seal ring 43 define a low pressure chamber 20 formed on the outer diameter side of the movable scroll 42 and a back pressure chamber 50 formed on the back side of the movable scroll 42 inside the inner casing 3. The back pressure chamber 50 is sealed between the rotary shaft 2 inserted through the through hole 3a by the seal ring 44 fixed to the inner periphery of the through hole 3a provided at the center of the inner casing 3, thereby forming a closed space.

[0040] In addition, a throttle hole (not shown) is provided in the back pressure communication passage 14 formed throughout the cover 12, the fixed scroll 41, and the inner shell 3, and connecting the high pressure chamber 30 and the back pressure chamber 50, and the refrigerant in the high pressure chamber 30 after the pressure reduction adjustment by the throttle hole is supplied to the back pressure chamber 50 together with the lubricating oil separated by the oil separator 6. At this time, the pressure in the back pressure chamber 50 is adjusted to be higher than the pressure in the low pressure chamber 20. It should be noted that a pressure release hole 16 is formed in the inner shell 3, which penetrates in the radial direction and connects the low pressure chamber 20 and the back pressure chamber 50, and a pressure regulating valve 45 is provided in the pressure release hole 16. When the pressure in the back pressure chamber 50 exceeds the set value, the pressure regulating valve 45 opens.

[0041] In addition, the boss 42c of the movable scroll 42 is inserted into the through hole 8b at the center of the thrust plate 8. The through hole 8b is formed to have a diameter that allows the eccentric portion 2a of the rotating shaft 2 inserted in the boss 42c to rotate eccentrically. That is, the sliding surface 7a of the side seal 7 can slide relative to the sliding surface 8a of the thrust plate 8 in conjunction with the eccentric rotation of the rotating shaft 2 (see Figure 3 ).

[0042] In addition, Figure 3 middle, Figure 3 (a) to (d) show the rotation trajectory of the boss 42c indicated by the black arrow when viewed from the fixed scroll 41 side. Figure 3 (a) is the reference in the counterclockwise direction, and the boss 42c is rotated 90 degrees, 180 degrees, and 270 degrees respectively. In addition, the sliding area of ​​the sliding surface 7a of the side seal 7 and the sliding surface 8a of the thrust plate 8 is schematically shown by dots. In addition, for the convenience of explanation, for the rotating shaft 2, only the eccentric portion 2a inserted in the boss 42c is shown, and the illustration of the counterweight portion 2b and the like constituting the eccentric mechanism is omitted.

[0043] Thus, the thrust plate 8 has the sliding surface 8 a that slides relatively with the sliding surface 7 a of the side seal 7 that rotates eccentrically.

[0044] In addition, an elastic member 9 is inserted between the side seal 7 and the scroll compression mechanism 4, more specifically, between the side seal 7 and the movable scroll 42 (see Figure 1), the difference in the axial position of the circumferential phase is absorbed by the dynamic pressure generated between the side seal 7 and the thrust plate 8, that is, the movable scroll 42 is prevented from tilting. It should be noted that the elastic member 9 can be a member that is deformed by a material such as an O-ring, or a member that is deformed in shape like a spring.

[0045] Next, refer to Figure 4 and Figure 5 The generation of dynamic pressure when the side seal 7 slides relative to the thrust plate 8 will be described.

[0046] In addition, Figure 4 and Figure 5 In Figure 3 The sliding state between a dynamic pressure generating portion 81A at the 12 o'clock position of the thrust plate 8 and the side seal 7 is described as an example. Figure 4 , the side seal 7 is shown relative to one dynamic pressure generating portion 81A. Figure 3 The state of (a) is towards Figure 3 (b) The way the state moves. Figure 5 , the side seal 7 is shown relative to one dynamic pressure generating portion 81A. Figure 3 The state of (c) is towards Figure 3 (d) The state of the moving state.

[0047] exist Figure 4 In the state, the side seal 7 overlaps with the first inclined groove group 85 in one dynamic pressure generating portion 81A in the axial direction. At this time, the side seal 7 slides relative to the dynamic pressure generating portion 81A in the counterclockwise direction.

[0048] As a result, the fluid F1 in the low pressure chamber 20 existing in each first inclined groove 851 of the first inclined groove group 85 moves from one end 851a to the other end 851b (see Figure 4 black arrow in the figure).

[0049] As a result, dynamic pressure is generated at the other end 851b, and the sliding surfaces 7a and 8a are slightly separated from each other, forming a fluid film based on the fluid F1. The fluid F1 in the low pressure chamber 20 is supplied to each first inclined groove 851 from the one end 851a at any time.

[0050] The fluid F1 flowing out from the other end 851b to between the sliding surfaces 7a and 8a moves toward the back pressure chamber 50. As a result, the fluid F2 in the back pressure chamber 50 is pushed back to the back pressure chamber 50 and becomes difficult to flow into between the sliding surfaces 7a and 8a (see Figure 4 In addition, a portion of the fluid F1 and a portion of the fluid F2 are stored in the recess 84.

[0050] exist Figure 5In the state, the side seal 7 overlaps with the second inclined groove group 86 in one dynamic pressure generating portion 81A in the axial direction. At this time, the side seal 7 slides relative to the dynamic pressure generating portion 81A in the counterclockwise direction.

[0052] As a result, the fluid in each second inclined groove 861 of the second inclined groove group 86 moves from one end 861a to the other end 861b (see Figure 5 black arrow in the figure).

[0053] Thus, dynamic pressure is generated at the other end 861b, and the sliding surfaces 7a and 8a are slightly separated from each other, forming a fluid film based on the fluid. In addition, the fluid in the recess 84 is supplied to each second inclined groove 861 from the one end 861a at any time.

[0054] It should be noted that in Figure 4 The status of Figure 5 When the state is transferred, the concave portion 84 gradually stops communicating with the back pressure chamber 50 side and communicates with the low pressure chamber 20 side. Therefore, among the fluids supplied from the concave portion 84 to the second inclined groove 861, the fluid F1 in the low pressure chamber 20 gradually increases. Figure 5 In the state, fluid F1 is almost supplied.

[0055] The fluid F1 flowing out from the other end 861b to between the sliding surfaces 7a and 8a moves toward the back pressure chamber 50. As a result, the fluid F2 in the back pressure chamber 50 is pushed back to the back pressure chamber 50 and becomes difficult to flow into between the sliding surfaces 7a and 8a (see Figure 5 (white arrow in the figure).

[0056] As described above, the thrust plate 8 has the dynamic pressure generating portion 81, which includes the first inclined groove group 85 located on the low pressure chamber 20 side, and the second inclined groove group 86 located on the back pressure chamber 50 side, and the second inclined groove 861 of the second inclined groove group 86 is not connected to the back pressure chamber 50 side. As a result, the fluid F2 of the back pressure chamber 50 having a higher pressure than the fluid F1 of the low pressure chamber 20 is restricted from entering between the sliding surfaces 7a and 8a, so that leakage of the fluid F2 to the low pressure chamber 20 can be suppressed.

[0057] In addition, since a recess 84 serving as a buffer space is formed between the first inclined groove group 85 and the second inclined groove group 86 , the fluid F1 flowing out from the first inclined groove group 85 to between the sliding surfaces 7 a and 8 a can be stored in the recess 84 , and the fluid F1 can be supplied from the recess 84 to the second inclined groove group 86 .

[0058] In addition, the recess 84 is arranged in the dynamic pressure generating portion 81, so that the fluid F1 can be stored without being affected by the separation distance between the sliding surfaces 7a and 8a, that is, the axial position of the thrust plate 8 and the side seal 7, so that dynamic pressure can be generated in the second inclined groove group 86 by the fluid F1 in the recess 84.

[0059] In addition, one end 861a of the second inclined groove 861 of the second inclined groove group 86 communicates with the recessed portion 84. Thus, the fluid F1 can be smoothly supplied from the recessed portion 84 to the second inclined groove 861 of the second inclined groove group 86.

[0060] In addition, since the one ends 851 a of the first inclined grooves 851 of the first inclined groove group 85 are in communication with the low pressure chamber 20 , the fluid F1 can be smoothly supplied from the low pressure chamber 20 to the first inclined grooves 851 .

[0061] The thrust plate 8 is configured such that the plurality of dynamic pressure generating portions 81 are continuously provided in an annular shape so that each second inclined groove group 86 is located on the back pressure chamber 50 side. This can prevent the fluid F2 in the back pressure chamber 50 from leaking toward the low pressure chamber 20 side in the circumferential direction. Example 2

[0062] Next, refer to Figure 6 A thrust support mechanism according to Embodiment 2 will be described. It should be noted that descriptions of the same and overlapping structures as those of Embodiment 1 will be omitted.

[0063] like Figure 6 As shown, the thrust plate 28 of the second embodiment is provided with a communication groove 287 that connects the recessed portion 284 with the low pressure chamber 20. The communication groove 287 is a concave groove that opens on the sliding surface 28a side.

[0064] Thus, the fluid F1 in the low pressure chamber 20 can be constantly introduced into the recessed portion 284 via the communication groove 287 . Therefore, the fluid F1 in the recessed portion 284 is not depleted, and stable sliding properties can be exhibited.

[0065] It should be noted that in this embodiment 2, the connecting groove 287 is illustrated as a groove opening on the sliding surface 28a side, but it is not limited to this. It can also be a hole that connects the side of the low-pressure chamber 20 side of the recess 284 with the side of the low-pressure chamber 20 side of the thrust plate 28.

[0066] As mentioned above, although the embodiment of the present invention is described based on the drawings, the specific structure is not limited to these embodiments, and the change and addition within the range which does not deviate from the summary of the present invention are also included in the present invention.

[0067] For example, in the above-mentioned embodiments 1 and 2, the manner in which all the second inclined grooves 861 in the second inclined groove group 86 are not connected to the back pressure chamber 50 side is illustrated, but some of the second inclined grooves 861 may be connected to the back pressure chamber. Preferably, the number of inclined grooves not connected to the back pressure chamber is greater than the number of inclined grooves connected to the back pressure chamber.

[0068] In addition, in the above-mentioned embodiments 1 and 2, the first groove and the second groove are illustrated as inclined grooves, but they may not be inclined grooves. That is, as long as they are grooves capable of generating dynamic pressure, known structures capable of generating dynamic pressure, such as grooves extending parallel to the circumferential direction and grooves with inclined bottom surfaces, may be used.

[0069] In addition, the thrust plates of the above-mentioned embodiments 1 and 2 are exemplified as a plurality of dynamic pressure generating parts connected in the circumferential direction to form an annular shape, but at least one dynamic pressure generating part may be provided. It should be noted that the thrust plate is not limited to an annular shape.

[0070] In the above-mentioned embodiments 1 and 2, the recessed portion as the buffer space is formed in the thrust plate, but a buffer space such as a recessed portion may be formed on the side seal. It should be noted that no buffer space may be provided between the first inclined groove group and the second inclined groove group.

[0071] Furthermore, in the above-mentioned Examples 1 and 2, the example in which the inclined grooves of the second inclined groove group communicate with the recessed portion is shown, but pits or the like which are not communicated with the recessed portion may also be used.

[0072] Furthermore, in the above-mentioned Embodiments 1 and 2, the inclined grooves of the first inclined groove group are exemplified as being in communication with the low pressure chamber, but pits or the like which are not in communication with the low pressure chamber may also be used.

[0073] In addition, in the above-mentioned embodiments 1 and 2, the method of applying the thrust plate as a thrust support mechanism to the scroll compressor C used in the air-conditioning system of an automobile, etc. is described, but it is not limited to this. As long as it is a rotating machine including an eccentric mechanism, it can also be applied to a scroll expansion compressor that includes an expander and a compressor in one body.

[0074] In the above-mentioned first and second embodiments, the outer diameter side of the thrust plate is described as the low pressure side and the inner diameter side as the high pressure side. However, the outer diameter side of the thrust plate may be the high pressure side and the inner diameter side may be the low pressure side.

[0075] Furthermore, the fluid in the spaces inside and outside the sliding surface of the thrust support mechanism may be in a gas, liquid, or a mixed state of gas and liquid.

[0076] In the above-mentioned first and second embodiments, the side seal having the sliding surface that slides relatively is made of resin and the thrust plate is made of metal. However, the material of the thrust support mechanism can be freely selected according to the use environment and the like.

[0077] Furthermore, in the above-mentioned first and second embodiments, the side seal slides relatively with respect to the thrust plate. However, the back surface of the movable scroll may directly slide relatively with respect to the thrust plate.

[0078] In the above-mentioned first and second embodiments, the thrust plate is fitted into the installation groove provided in the inner shell and arranged in a rotation-restricted state, but the present invention is not limited to this. For example, the thrust plate may be fixed to the inner shell in a non-rotatable manner by bolts or the like. Description of Reference Numerals

[0079] 4: scroll compression mechanism; 7: side seal; 7a: sliding surface (back side sliding surface); 8: thrust plate (thrust support mechanism); 8a: sliding surface; 20: low pressure chamber (low pressure side); 28: thrust plate; 28a: sliding surface; 41: fixed scroll disk; 42: movable scroll disk; 50: back pressure chamber (high pressure side); 81, 81A: dynamic pressure generating part; 84: recess; 85: first inclined groove group; 86: second inclined groove group; 284: recess; 287: connecting groove; 851: first inclined groove; 861: second inclined groove; C: scroll compressor; F1, F2: fluid.

Claims

1. A thrust support mechanism, the thrust support mechanism being provided on the back side of a movable scroll that slides relative to a fixed scroll with eccentric rotation, and capable of generating dynamic pressure on the back side of the movable scroll, wherein: The thrust support mechanism has a dynamic pressure generating portion including a first groove communicating with a low pressure side and a second groove communicating with a buffer space between an inner diameter end and an outer diameter end of the thrust support mechanism.

2. The thrust support mechanism according to claim 1, wherein: The buffer space is a recessed portion.

3. The thrust support mechanism according to claim 2, wherein: The recessed portion communicates with the low-pressure side.

4. The thrust bearing mechanism according to any one of claims 1 to 3, wherein: In the thrust support mechanism, the dynamic pressure generating portions having a smaller diameter than the diameter of the thrust support mechanism are evenly arranged at intervals in a circumferential direction of the thrust support mechanism.

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