sliding member

Abstract

Provided is a sliding member capable of stably reducing frictional resistance between sliding surfaces accompanying eccentric rotation. A sliding member (8) having sliding surfaces (8a) that slide relative to each other accompanying eccentric rotation, wherein a plurality of dynamic pressure generation grooves (80) are provided on the sliding surfaces (8a) in the circumferential direction, the dynamic pressure generation grooves (80) extending in a manner in which the leading end gradually tapers toward the direction of relative eccentric rotation with respect to the opposing sliding surface (7a).

Description

TECHNICAL FIELD

[0001] The present application relates to a sliding member used in a rotary machine including an eccentric mechanism. BACKGROUND

[0002] Machines accompanied by a rotary drive used in various industrial fields not only have a rotary machine in which a center shaft is kept in a fixed position and rotates, but also a rotary machine in which a center shaft rotates with eccentricity. As one of the rotary machines that rotate with eccentricity, there are scroll compressors and the like, which are mechanisms that have a scroll compression mechanism composed of a fixed scroll having scroll teeth in the front surface of an end plate and a movable scroll having scroll teeth in the front surface of an end plate, an eccentric mechanism that makes a rotary shaft eccentrically rotate, and the like, and that make the movable scroll relatively slide with respect to the fixed scroll while rotating with eccentricity by the rotation of the rotary shaft, thereby pressurizing a fluid supplied from a low-pressure chamber on the outer diameter side of the two scrolls and discharging a high-pressure fluid from a discharge hole formed in the center of the fixed scroll.

[0003] These scroll compressors that utilize the mechanism of making the movable scroll relatively slide with respect to the fixed scroll while rotating with eccentricity not only have high compression efficiency, but also have low noise, and thus are used in various applications such as refrigeration cycles, but there is a problem that refrigerant leaks from the axial gap between the two scrolls. In the scroll compressor shown in Patent Literature 1, a thrust plate that relatively slides with the movable scroll is provided on the back surface side of the movable scroll, a portion of the refrigerant compressed by the scroll compression mechanism is supplied to a back pressure chamber formed on the back surface side of the thrust plate, and the movable scroll is pressed toward the fixed scroll, whereby it is possible to reduce the leakage of the refrigerant from the axial gap between the two scrolls when the refrigerant is compressed.

[0004] PRIOR ART DOCUMENTS

[0005] PATENT LITERATURE

[0006] Patent Literature 1: Japanese Patent Application Laid-Open No. 2016-61208 (p. 5 to p. 6, Figure 1 ) SUMMARY

[0007] PROBLEMS TO BE SOLVED BY THE INVENTION

[0008] However, in the scroll compressor shown in Patent Literature 1, a part of the refrigerant compressed by the scroll compressor is used to press the movable scroll toward the fixed scroll from the back side via the thrust plate, so although it is possible to reduce the case where the refrigerant leaks from the axial gap between the two scrolls, in the two scrolls, particularly on the sliding surface of the movable scroll and the thrust plate that rotates eccentrically, the pressing force acts from both axial sides, so there is a problem in that the frictional resistance becomes large, the smooth movement of the movable scroll is hindered, and the compression efficiency cannot be improved.

[0009] The present application was completed in view of such a problem, and aims to provide a sliding member capable of stably reducing the frictional resistance between sliding surfaces that rotate eccentrically.

[0010] Means for solving the problem

[0011] To solve the above problem, the sliding member of the present application has sliding surfaces that slide relative to each other with eccentric rotation, wherein a plurality of dynamic pressure generating grooves are provided on the sliding surfaces in the circumferential direction, and the dynamic pressure generating grooves extend in a manner in which the front end gradually tapers toward the downstream side in the relative eccentric rotation direction with respect to the opposite sliding surface.

[0012] Thus, when the opposite sliding surface slides relative to the sliding surface with eccentric rotation, the fluid in the dynamic pressure generating groove is gathered in the tapered portion in the dynamic pressure generating groove that tapers toward the downstream side in the relative eccentric rotation direction between the sliding surface and the opposite sliding surface, and dynamic pressure can be reliably generated at the position on the downstream side in the relative eccentric rotation direction of the dynamic pressure generating groove. Thus, the sliding surfaces are separated from each other, the lubricity is improved, and the frictional resistance between the sliding surfaces can be reduced.

[0013] It can also be that the end portion on the downstream side in the eccentric rotation direction of the dynamic pressure generating groove is an angular portion that tapers at an acute angle.

[0014] Thus, the fluid in the dynamic pressure generating groove is gathered in the angular portion that tapers at an acute angle, and large dynamic pressure can be generated at the angular portion.

[0015] It can also be that the dynamic pressure generating groove communicates with the external space of the sliding surface.

[0016] Thus, fluid can be introduced from the external space into the dynamic pressure generating groove, so dynamic pressure can be reliably generated in the dynamic pressure generating groove.

[0017] It can also be that the sliding surface and the opposite sliding surface slide with eccentric rotation in a manner in which the opposite sliding surface overlaps with a part of the plurality of dynamic pressure generating grooves, and the opposite sliding surface does not overlap with the other dynamic pressure generating grooves.

[0018] Thus, in the relative sliding of the sliding surface and the opposing sliding surface accompanying eccentric rotation, no dynamic pressure is generated in the other dynamic pressure generating grooves of the plurality of dynamic pressure generating grooves of the sliding surface that do not overlap the opposing sliding surface, and dynamic pressure is generated only in the part of the plurality of dynamic pressure generating grooves of the sliding surface that overlap the opposing sliding surface. Thus, it is possible to prevent the generation of an undesirable negative pressure in the other dynamic pressure generating grooves.

[0019] Also, a plurality of the dynamic pressure generating grooves can be provided on at least one of the inner diameter side and the outer diameter side of the sliding surface in the circumferential direction, and a plurality of other dynamic pressure generating grooves can be provided on the other of the inner diameter side and the outer diameter side of the sliding surface in the circumferential direction, the other dynamic pressure generating grooves extending in a manner in which the leading end is tapered toward the downstream side in the relative eccentric rotation direction opposite to the opposing sliding surface.

[0020] Thus, it is possible to generate dynamic pressure on the outer diameter side and the inner diameter side of the sliding surface by the respective dynamic pressure generating grooves.

[0021] Also, the tapered portions of the dynamic pressure generating grooves and the tapered portions of the other dynamic pressure generating grooves that are adjacent in the radial direction can be formed to face in opposite directions in the eccentric rotation direction.

[0022] Thus, it is possible to generate dynamic pressure at the tapered portions of the dynamic pressure generating grooves and the tapered portions of the other dynamic pressure generating grooves that are adjacent in the radial direction, and thus separate the sliding surfaces in a state in which tilting is suppressed.

[0023] Also, the dynamic pressure generating grooves and the other dynamic pressure generating grooves can be separated in the radial direction, and the separation width can be greater than the radial width of the annular opposing sliding surface that slides relative to the sliding surface.

[0024] Thus, the annular opposing sliding surface is not provided across the dynamic pressure generating grooves and the other dynamic pressure generating grooves that are adjacent in the radial direction, and it is thus possible to prevent the simultaneous generation of positive pressure and negative pressure in the dynamic pressure generating grooves and the other dynamic pressure generating grooves that are adjacent in the radial direction.

[0025] Also, a plurality of non-communicating grooves can be provided between the dynamic pressure generating grooves and the other dynamic pressure generating grooves in the circumferential direction, the non-communicating grooves being surrounded by land portions that divide the dynamic pressure generating grooves and the other dynamic pressure generating grooves.

[0026] Thus, the opposing sliding surface that performs eccentric rotation motion overlaps any of the dynamic pressure generating grooves, the other dynamic pressure generating grooves, or the non-communicating grooves over the entire circumferential range, and thus it is possible to generate dynamic pressure between the sliding surfaces over the entire circumferential range regardless of the relative positions of the sliding surface and the opposing sliding surface.

[0027] It can also be that the non-communicating grooves are provided in a plurality along the radial direction between the dynamic pressure generating groove and the other dynamic pressure generating groove adjacent in the radial direction, each of the non-communicating grooves having a different shape.

[0028] Thus, the generated dynamic pressure can be changed in correspondence with the relative position of the sliding surface and the counter sliding surface. BRIEF DESCRIPTION OF DRAWINGS

[0029] Figure 1 is a diagram showing a sliding surface of a thrust plate as a sliding member of a scroll compressor to which Embodiment 1 of the present application is applied.

[0030] Figure 2 is a diagram showing a sliding surface of a thrust plate of Embodiment 1 of the present application.

[0031] Figure 3 (a) of FIG. 1 is an enlarged view of a dynamic pressure generating groove, Figure 3 (b) of FIG. 1 is a cross-sectional view taken along line A-A.

[0032] Figure 4 is a diagram showing relative sliding of a sliding surface of a side seal and a sliding surface of a thrust plate of Embodiment 1 of the present application. In addition, in Figure 4 (a) of FIG. 2 shows a position relationship between the sliding surface of the side seal and the sliding surface of the thrust plate at the start position, Figure 4 (b) of FIG. 2 shows a position relationship between the sliding surface of the side seal and the sliding surface of the thrust plate at the time when the rotational shaft is eccentrically rotated to 90 degrees, Figure 4 (c) of FIG. 2 shows a position relationship between the sliding surface of the side seal and the sliding surface of the thrust plate at the time when the rotational shaft is eccentrically rotated to 180 degrees, Figure 4 (d) of FIG. 2 shows a position relationship between the sliding surface of the side seal and the sliding surface of the thrust plate at the time when the rotational shaft is eccentrically rotated to 270 degrees.

[0033] Figure 5 is a diagram showing a position of generation of dynamic pressure generated in the dynamic pressure generating groove with respect to the state of Figure 4 (a) of FIG. 3 toward Figure 4 (b) of FIG. 3.

[0034] Figure 6 is a diagram showing a position of generation of dynamic pressure generated in the dynamic pressure generating groove with respect to the state of Figure 4 (c) of FIG. 4 toward Figure 4 (d) of FIG. 4.

[0035] Figure 7 is a diagram showing a sliding surface of a thrust plate of Embodiment 2 of the present application.

[0036] Figure 8This is a diagram showing the sliding surface of the thrust plate in Embodiment 3 of the present invention.

[0037] Figure 9 This is a diagram showing the sliding surface of the thrust plate in Embodiment 4 of the present invention.

[0038] Figure 10 This is a diagram showing the sliding surface of the thrust plate in Embodiment 5 of the present invention.

[0039] Figure 11 This is a diagram showing the sliding surface of the thrust plate according to Embodiment 6 of the present invention.

[0040] Figure 12 This is a diagram showing the sliding surface of the thrust plate according to Embodiment 7 of the present invention.

[0041] Figure 13 This is a diagram showing the sliding surface of the thrust plate according to Embodiment 8 of the present invention. Detailed Implementation

[0042] Hereinafter, the method of implementing the sliding component of the present invention will be described based on embodiments.

[0043] Example 1

[0044] Reference Figures 1 to 6 Regarding the sliding component of Embodiment 1. Furthermore, for ease of explanation, the grooves and the like formed on the sliding surface of the sliding component are marked with points in the accompanying drawings.

[0045] The sliding component of the present invention is applicable to rotating machinery containing an eccentric mechanism, such as a scroll compressor C used in air conditioning systems of automobiles to draw in, compress, and eject a refrigerant as a fluid. Furthermore, in this embodiment, the refrigerant is a gas mixed with a mist of lubricating oil.

[0046] First, let's explain the scroll compressor C. For example... Figure 1 As shown, the scroll compressor C mainly comprises a housing 1, a rotating shaft 2, an inner shell 3, a scroll compression mechanism 4, a side seal 7, a thrust plate 8 as a sliding component, and a drive motor M.

[0047] The housing 1 has a cylindrical outer shell 11 and a cover 12. The cover 12 closes the opening of the outer shell 11. In addition, the opening on the axially opposite side of the opening of the outer shell 11 that is closed by the cover 12 is closed by a drive motor M.

[0048] A low-pressure chamber 20, a high-pressure chamber 30, and a back-pressure chamber 50 are formed inside the housing 11. A low-pressure refrigerant is supplied from a refrigerant circuit not shown to the low-pressure chamber 20, which is an outside space on the low-pressure side, through the suction port 10. The high-pressure chamber 30 is sprayed with a high-pressure refrigerant compressed by the scroll compressor mechanism 4. The back-pressure chamber 50, which is an outside space on the high-pressure side, is supplied with lubricating oil and a portion of the refrigerant compressed by the scroll compressor mechanism 4. In addition, the back-pressure chamber 50 is formed inside a cylindrical inner housing 3, which is housed inside the housing 11.

[0049] A spray communication passage 13 is formed in the cover 12. The spray communication passage 13 communicates the refrigerant circuit not shown and the high-pressure chamber 30. In addition, a portion of a back-pressure communication passage 14, which communicates the high-pressure chamber 30 and the back-pressure chamber 50, is formed in the cover 12, branching from the spray communication passage 13. In addition, an oil separator 6, which separates lubricating oil from refrigerant, is provided on the spray communication passage 13.

[0050] The inner housing 3 is fixed in a state in which the axial end portions thereof abut against an end plate 41a of a fixed scroll 41 constituting the scroll compressor mechanism 4. In addition, a suction communication passage 15, which penetrates in the radial direction, is formed in the side wall of the inner housing 3. That is, the low-pressure chamber 20 is formed from the outside of the inner housing 3 to the inside of the inner housing 3 via the suction communication passage 15. The refrigerant supplied to the inside of the inner housing 3 through the suction communication passage 15 is sucked into the scroll compressor mechanism 4.

[0051] The scroll compressor mechanism 4 mainly has the fixed scroll 41 and a movable scroll 42. The fixed scroll 41 is fixed to the cover 12 in a substantially sealed state. The movable scroll 42 is housed inside the inner housing 3.

[0052] The fixed scroll 41 is made of metal and has scroll teeth 41b in a scroll shape. The scroll teeth 41b in a scroll shape are provided projecting from the front surface of the end plate 41a toward the movable scroll 42. In addition, a recessed portion 41c, in which the inner diameter side of the end surface of the end plate 41a, which abuts against the cover 12, is recessed in a direction opposite to the cover 12, is formed in the fixed scroll 41. The high-pressure chamber 30 is divided by the recessed portion 41c and the cover 12.

[0053] The movable scroll 42 is made of metal and has scroll teeth 42b in a scroll shape. The scroll teeth 42b in a scroll shape are provided projecting from the front surface of the end plate 42a toward the fixed scroll 41. In addition, a protruding portion 42c, which protrudes from the center of the back surface of the end plate 42a, is formed in the movable scroll 42. The eccentric portion 2a of the rotating shaft 2 is relatively rotatably fitted in the protruding portion 42c. In addition, in this embodiment, the eccentric mechanism, which eccentrically rotates the rotating shaft 2, is constituted by the eccentric portion 2a of the rotating shaft 2 and the counterweight portion 2b, which protrudes in the outer diameter direction from the rotating shaft 2.

[0054] When the rotation shaft 2 is rotationally driven by the drive motor M, the eccentric portion 2a performs eccentric rotation, and the movable scroll 42 relatively slides with respect to the fixed scroll 41 in a state of maintaining the posture while following the eccentric rotation. At this time, the movable scroll 42 performs eccentric rotation with respect to the fixed scroll 41, and in conjunction with this rotation, the contact positions of the scroll teeth 41b, 42b move in the rotation direction in order, and the compression chambers 40 formed between the scroll teeth 41b, 42b move toward the center while gradually reducing. Thus, the refrigerant sucked from the low-pressure chamber 20 formed on the outer diameter side of the scroll type compression mechanism 4 is compressed into the compression chambers 40, and finally, 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.

[0055] Next, the side seal 7 will be described. The side seal 7 is made of resin, has a rectangular shape in cross section, and is circular in shape when viewed in the axial direction (see FIG. 2). The side seal 7 is fixed to the back surface of the end plate 42a of the movable scroll 42. Figure 4 In addition, the side seal 7 is fixed to the back surface of the end plate 42a of the movable scroll 42.

[0056] The side seal 7 has a sliding surface 7a that abuts against the sliding surface 8a of the thrust plate 8 as an opposing sliding surface, and the sliding surface 7a is formed as a flat surface without forming a concave-convex or the like.

[0057] Next, the thrust plate 8 as a sliding member of the present embodiment will be described. In addition, in (b) of FIG. 8, a state in which a cross-sectional view along the A-A line is linearly expanded is illustrated for convenience of explanation. Figure 3

[0058] Referring to Figure 2 and Figure 3 , the thrust plate 8 is made of metal and is circular in shape. The sliding surface 8a that abuts against the sliding surface 7a (see Figure 1 ) of the side seal 7 is formed on the thrust plate 8.

[0059] As shown in Figure 2 , the sliding surface 8a of the thrust plate 8 has an outer dynamic pressure generation groove 80, an inner dynamic pressure generation groove 81, and a land portion 82. The outer dynamic pressure generation groove 80 as a dynamic pressure generation groove is provided on the outer diameter side of the sliding surface 8a. The inner dynamic pressure generation groove 81 as another dynamic pressure generation groove is provided on the inner diameter side of the sliding surface 8a. The land portion 82 divides the outer dynamic pressure generation groove 80 and the inner dynamic pressure generation groove 81.

[0060] The outer dynamic pressure generation groove 80 extends obliquely with respect to the circumferential direction from the outer diameter end edge of the sliding surface 8a toward the inner diameter side. In addition, the outer dynamic pressure generation groove 80 communicates with the low-pressure chamber 20 (see Figure 1 ) as an outer space on the outer diameter side. ​

[0061] Specifically, the outer dynamic pressure generating groove 80 is divided by side walls 80a, 80b, an inner end wall 80c, and a bottom wall 80d. The side walls 80a, 80b extend in the depth direction in a manner perpendicular to the flat surface 82a of the land portion 82, and extend obliquely with respect to the circumferential direction from the outer diameter end edge of the sliding surface 8a toward the inner diameter side in the counterclockwise direction. The inner end wall 80c joins the inner diameter end portions of the side walls 80a, 80b to each other. The bottom wall 80d extends in parallel with the surface 82a, and joins the depth direction end portions of the side walls 80a, 80b and the inner end wall 80c to each other.

[0062] The inner end wall 80c is shorter than the side walls 80a, 80b, and extends substantially along the circumferential direction. In addition, the component of the inner end wall 80c that is oblique with respect to the circumferential direction is smaller than the component of the side walls 80a, 80b that is oblique with respect to the circumferential direction.

[0063] In addition, the corner portion 80e, which is formed by the side wall 80a and the inner end wall 80c, is an acute angle, and the corner portion 80f, which is formed by the side wall 80b and the inner end wall 80c, is an obtuse angle.

[0064] That is, the outer dynamic pressure generating groove 80 extends in a manner in which the front end tapers toward the counterclockwise direction. In other words, the corner portion 80e functions as a tapered portion of the outer dynamic pressure generating groove 80. In addition, tapering of the front end toward the counterclockwise direction (i.e., the downstream side in the eccentric rotation direction) means that the angle formed by the two side walls of each groove that are opposite the eccentric rotation direction (i.e., the two side walls that are opposite the circumferential component and the radial component of the eccentric rotation direction in any state) is less than 180°. By the presence of the angle that is less than 180°, fluid is gathered, and dynamic pressure can be generated, and in the case where the angle is an acute angle, fluid does not easily escape from the groove, and dynamic pressure can be efficiently generated.

[0065] On the other hand, the inner dynamic pressure generating groove 81 extends obliquely in the circumferential direction from the inner diameter end edge of the sliding surface 8a toward the outer diameter side. In addition, the inner dynamic pressure generating groove 81 communicates with the back pressure chamber 50 (refer to Figure 1 ) that is the outer space on the inner diameter side.

[0066] Specifically, the inner dynamic pressure generating groove 81 is divided by side walls 81a, 81b, an outer end wall 81c, and a bottom wall 81d. The side walls 81a, 81b extend in the depth direction in a manner perpendicular to the flat surface 82a of the land portion 82. In addition, the side walls 81a, 81b extend obliquely with respect to the circumferential direction from the inner diameter end edge of the sliding surface 8a toward the outer diameter side in the clockwise direction. The outer end wall 81c joins the outer diameter end portions of the side walls 81a, 81b to each other. The bottom wall 81d extends in parallel with the surface 82a, and joins the depth direction end portions of the side walls 81a, 81b and the outer end wall 81c to each other.

[0067] The outer end wall 81c is shorter than the side walls 81a and 81b, and extends approximately circumferentially. Furthermore, the inclination component of the outer end wall 81c is smaller than that of the side walls 81a and 81b. Additionally, the angle 81e formed by the side wall 81a and the outer end wall 81c is an acute angle, and the angle 81f formed by the side wall 81b and the outer end wall 81c is an obtuse angle.

[0068] That is, the inner dynamic pressure generating groove 81 extends in a clockwise direction and gradually tapers at the front end. In other words, the acute-angled corner 81e functions as the tapering part of the inner dynamic pressure generating groove 81, and the tapering parts of the outer dynamic pressure generating groove 80 and the inner dynamic pressure generating groove 81 are oriented in opposite directions in the circumferential direction.

[0069] like Figure 3 As shown in (a) and (b), the width dimension L1 of the external dynamic pressure generating groove 80 (i.e., the separation width of the sidewalls 80a and 80b) is formed to be larger than the depth dimension L2 of the external dynamic pressure generating groove 80 (L1>L2). In addition, here, the width dimension of the opening of the external dynamic pressure generating groove 80 is shown as the width dimension L1 of the external dynamic pressure generating groove 80.

[0070] Furthermore, the width dimension L3 of the internal dynamic pressure generating groove 81 (i.e., the separation width of the sidewalls 81a and 81b) is formed to be larger than the depth dimension L4 of the internal dynamic pressure generating groove 81 (L3>L4). Here, the width dimension of the opening of the internal dynamic pressure generating groove 81 is shown as the width dimension L3 of the internal dynamic pressure generating groove 81.

[0071] Furthermore, as long as the width of the external dynamic pressure generating groove 80 and the internal dynamic pressure generating groove 81 is larger than its depth, the width and depth dimensions of the external dynamic pressure generating groove 80 and the internal dynamic pressure generating groove 81 can be freely changed. However, it is preferable that the width dimensions L1 and L3 are at least 10 times the depth dimensions L2 and L4. Additionally, the width dimensions L1 and L3 can be the same or different. Similarly, the depth dimensions L2 and L4 can be the same or different.

[0072] In addition, the inner end wall 80c of the external dynamic pressure generating groove 80 and the outer end wall 81c of the internal dynamic pressure generating groove 81 are separated in the radial direction, and the radial separation width L5 between the external dynamic pressure generating groove 80 and the internal dynamic pressure generating groove 81 is formed to be larger than the radial width L6 of the sliding surface 7a of the side seal 7 (L5>L6).

[0073] Reference Figure 1 A sealing ring 43 is fixed on the thrust plate 8. The sealing ring 43 abuts against the inner circumferential surface of the inner shell 3 on the surface opposite to the axial direction of the sliding surface 8a. Thus, the thrust plate 8 functions as a thrust bearing, bearing the axial load of the movable scroll plate 42 via the side seal 7.

[0074] Furthermore, the side seal 7 and the sealing ring 43 divide the interior of the inner shell 3 into a low-pressure chamber 20 formed on the outer diameter side of the movable scroll plate 42 and a back-pressure chamber 50 formed on the back side of the movable scroll plate 42. The back-pressure chamber 50 is a sealed space formed between the inner shell 3 and the rotating shaft 2. The sealing ring 44 is fixed to the inner circumference of the through hole 3a located at the center of the other end of the inner shell 3, and slides in a sealed manner with the rotating shaft 2 inserted through the through hole 3a. In addition, a back-pressure connecting passage 14 connecting the high-pressure chamber 30 and the back-pressure chamber 50 is formed by passing through the cover 12, the fixed scroll plate 41, and the inner shell 3. In addition, a throttling orifice (not shown) is provided on the back-pressure connecting passage 14, and the refrigerant in the high-pressure chamber 30 after pressure reduction adjustment by the throttling orifice, together with the lubricating oil separated by the oil separator 6, is supplied to the back-pressure chamber 50. 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. Additionally, a pressure relief port 16 is formed on the inner shell 3, which radially extends and connects the low-pressure chamber 20 and the back-pressure chamber 50. Furthermore, a pressure regulating valve 45 is provided within the pressure relief port 16. When the pressure in the back-pressure chamber 50 exceeds a set value, the pressure regulating valve 45 opens.

[0075] Furthermore, a protrusion 42c of a movable scroll plate 42 is inserted through the through hole 8b in the center of the thrust plate 8. The through hole 8b is formed to allow eccentric rotation caused by the eccentric portion 2a of the rotating shaft 2 inserted into the protrusion 42c. That is, the sliding surface 7a of the side seal 7 can slide relative to the sliding surface 8a of the thrust plate 8 with the eccentric rotation of the rotating shaft 2 (see reference). Figure 4 ).

[0076] In addition, Figure 4 middle, Figure 4 Figures (a) to (d) show the rotation trajectory of the protrusion 42c as viewed from the side of the fixed scroll plate 41, where the protrusion 42c... Figure 4 (a) is used as a reference to show the states after being rotated counterclockwise by 90 degrees, 180 degrees, and 270 degrees respectively. Additionally, the sliding areas of the sliding surface 7a of the side seal 7 and the sliding surface 8a of the thrust plate 8 are schematically shown with dots. Furthermore, for ease of explanation, only the eccentric portion 2a inserted into the protrusion 42c is shown for the rotating shaft 2; the illustrations of the counterweight portion 2b, etc., constituting the eccentric mechanism, are omitted.

[0077] Thus, the thrust plate 8 is a sliding component having a sliding surface 8a that slides relative to the sliding surface 7a of the side seal 7 by eccentric rotation.

[0078] Further, in the following, when the thrust plate 8 is taken as a pointer type clock, with the paper surface directly above as the 12 o'clock position, the plurality of outer dynamic pressure generating grooves near the 12 o'clock on the sliding surface 8a is referred to as outer dynamic pressure generating grooves 80A, the plurality of outer dynamic pressure generating grooves near the 3 o'clock is referred to as outer dynamic pressure generating grooves 80B, the plurality of outer dynamic pressure generating grooves near the 6 o'clock is referred to as outer dynamic pressure generating grooves 80C, and the plurality of outer dynamic pressure generating grooves near the 9 o'clock is referred to as outer dynamic pressure generating grooves 80D. Further, the plurality of inner dynamic pressure generating grooves near the 12 o'clock on the sliding surface 8a is referred to as inner dynamic pressure generating grooves 81A, the plurality of inner dynamic pressure generating grooves near the 3 o'clock is referred to as inner dynamic pressure generating grooves 81B, the plurality of inner dynamic pressure generating grooves near the 6 o'clock is referred to as inner dynamic pressure generating grooves 81C, and the plurality of inner dynamic pressure generating grooves near the 9 o'clock is referred to as inner dynamic pressure generating grooves 81D.

[0079] Specifically, in the state of (a) of FIG. 8, Figure 4 the sliding surface 7a overlaps with the plurality of outer dynamic pressure generating grooves 80A on the sliding surface 8a from the 10 o'clock to the vicinity of the 2 o'clock. The sliding surface 7a does not overlap with the outer dynamic pressure generating grooves 80B and the inner dynamic pressure generating grooves 81B on the sliding surface 8a near the 3 o'clock, and the land 82 is disposed between the outer dynamic pressure generating grooves 80B and the inner dynamic pressure generating grooves 81B. The sliding surface 7a overlaps with the plurality of inner dynamic pressure generating grooves 81C on the sliding surface 8a from the 4 o'clock to the vicinity of the 8 o'clock. The sliding surface 7a does not overlap with the outer dynamic pressure generating grooves 80D and the inner dynamic pressure generating grooves 81D on the sliding surface 8a near the 9 o'clock, and the land 82 is disposed between the outer dynamic pressure generating grooves 80D and the inner dynamic pressure generating grooves 81D.

[0080] That is, in the state of (a) of FIG. 8, Figure 4 the sliding surface 7a overlaps with a part of the outer dynamic pressure generating grooves 80A, and does not overlap with the other outer dynamic pressure generating grooves 80B to 80D. Further, the sliding surface 7a overlaps with a part of the inner dynamic pressure generating grooves 81C, and does not overlap with the other inner dynamic pressure generating grooves 81A, 81B, and 81D.

[0081] Further, in the state of (b) of FIG. 8, Figure 4 the sliding surface 7a does not overlap with the outer dynamic pressure generating grooves 80A and the inner dynamic pressure generating grooves 81A on the sliding surface 8a near the 12 o'clock, and the land 82 is disposed between the outer dynamic pressure generating grooves 80A and the inner dynamic pressure generating grooves 81A. The sliding surface 7a overlaps with the plurality of inner dynamic pressure generating grooves 81B on the sliding surface 8a from the 1 o'clock to the vicinity of the 5 o'clock. The sliding surface 7a does not overlap with the outer dynamic pressure generating grooves 80C and the inner dynamic pressure generating grooves 81C on the sliding surface 8a near the 6 o'clock, and the land 82 is disposed between the outer dynamic pressure generating grooves 80C and the inner dynamic pressure generating grooves 81C. The sliding surface 7a overlaps with the plurality of outer dynamic pressure generating grooves 80D on the sliding surface 8a from the 7 o'clock to the vicinity of the 11 o'clock.

[0082] That is, in Figure 4 In state (b), the sliding surface 7a overlaps with a portion of the external dynamic pressure generating groove 80D, but does not overlap with other external dynamic pressure generating grooves 80A to 80C. Furthermore, the sliding surface 7a overlaps with a portion of the internal dynamic pressure generating groove 81B, but does not overlap with other internal dynamic pressure generating grooves 81A, 81C, and 81D.

[0083] In addition, Figure 4 In state (c), at the location near the 10 o'clock to 2 o'clock position on the sliding surface 8a, the sliding surface 7a overlaps with multiple internal dynamic pressure generating grooves 81A. At the location near the 3 o'clock position on the sliding surface 8a, the sliding surface 7a does not overlap with the external dynamic pressure generating groove 80B and the internal dynamic pressure generating groove 81B, and is disposed in the land portion 82 between the external dynamic pressure generating groove 80B and the internal dynamic pressure generating groove 81B. At the location near the 4 o'clock to 8 o'clock position on the sliding surface 8a, the sliding surface 7a overlaps with multiple external dynamic pressure generating grooves 80C. At the location near the 9 o'clock position on the sliding surface 8a, the sliding surface 7a does not overlap with the external dynamic pressure generating groove 80D and the internal dynamic pressure generating groove 81D, and is disposed in the land portion 82 between the external dynamic pressure generating groove 80D and the internal dynamic pressure generating groove 81D.

[0084] That is, in Figure 4 In state (c), the sliding surface 7a overlaps with a portion of the external dynamic pressure generating groove 80C, but does not overlap with other external dynamic pressure generating grooves 80A, 80B, and 80D. Furthermore, the sliding surface 7a overlaps with a portion of the internal dynamic pressure generating groove 81A, but does not overlap with other internal dynamic pressure generating grooves 81B to 81D.

[0085] In addition, Figure 4 In state (d), near the 12 o'clock position on the sliding surface 8a, the sliding surface 7a does not overlap with the external dynamic pressure generating groove 80A and the internal dynamic pressure generating groove 81A, and is disposed in the land portion 82 between the external dynamic pressure generating groove 80A and the internal dynamic pressure generating groove 81A. Near the 1 o'clock to 5 o'clock position on the sliding surface 8a, the sliding surface 7a overlaps with multiple external dynamic pressure generating grooves 80B. Near the 6 o'clock position on the sliding surface 8a, the sliding surface 7a does not overlap with the external dynamic pressure generating groove 80C and the internal dynamic pressure generating groove 81C, and is disposed in the land portion 82 between the external dynamic pressure generating groove 80C and the internal dynamic pressure generating groove 81C. Near the 7 o'clock to 11 o'clock position on the sliding surface 8a, the sliding surface 7a overlaps with multiple internal dynamic pressure generating grooves 81A.

[0086] That is, in Figure 4In state (d), the sliding surface 7a overlaps with a portion of the external dynamic pressure generating groove 80B, but does not overlap with other external dynamic pressure generating grooves 80A, 80C, and 80D. Furthermore, the sliding surface 7a overlaps with a portion of the internal dynamic pressure generating groove 81D, but does not overlap with other internal dynamic pressure generating grooves 81A to 81C.

[0087] In this way, corresponding to the eccentric rotation angle of the sliding surface 7a, the positions of the outer dynamic pressure generating grooves 80A to 80D and the inner dynamic pressure generating grooves 81A to 81D that overlap with the sliding surface 7a move continuously on the sliding surface 8a.

[0088] Next, refer to Figure 5 and Figure 6 The generation of dynamic pressure when the thrust plate 8 and the side seal 7 slide relative to each other is explained. Additionally, in Figure 5 The side seal 7 is shown in the image. Figure 4 The state of (a) is towards Figure 4 The form of state (b) during movement, in Figure 6 The text shows from Figure 4 The state of (c) is towards Figure 4 The form of (d) when it moves. Additionally, in Figure 5 and Figure 6 The diagram shows the thrust plate 8 as viewed from the side of the fixed scroll plate 41. The circle markings shown in the enlarged section indicate the locations where the pressure increases in the external dynamic pressure generating groove 80 and the internal dynamic pressure generating groove 81.

[0089] like Figure 5 As shown, when the side seal 7 moves in the direction of the white arrow, dynamic pressure is generated in multiple external dynamic pressure generating grooves 80A and multiple internal dynamic pressure generating grooves 81C.

[0090] Specifically, when the side seal 7 moves in the direction of the white arrow, the fluid in the external dynamic pressure generating groove 80A moves in the direction of the white arrow, i.e., the eccentric rotation direction of the sliding surface 7a, and accumulates at the acute corner 80e, generating a large dynamic pressure at the corner 80e. Similarly, in the internal dynamic pressure generating groove 81C, the fluid in the internal dynamic pressure generating groove 81C moves in the direction of the white arrow, accumulates at the acute corner 81e, and generates a large dynamic pressure at the corner 81e.

[0091] In this way, large dynamic pressure can be generated at the corner 80e of the external dynamic pressure generating groove 80A and the corner 81e of the internal dynamic pressure generating groove 81C, causing the sliding surfaces 7a and 8a to separate from each other. As a result, a fluid film composed of fluid is formed between the sliding surfaces 7a and 8a, which can reduce the frictional resistance between the sliding surfaces 7a and 8a.

[0092] Further, when the fluid in the outer dynamic pressure generating groove 80A and the inner dynamic pressure generating groove 81C moves in the eccentric rotation direction of the sliding surface 7a, the fluid in the low pressure chamber 20 is introduced into the outer dynamic pressure generating groove 80A through the outer diameter side opening of the outer dynamic pressure generating groove 80A, and the fluid in the back pressure chamber 50 is introduced into the inner dynamic pressure generating groove 81C through the inner diameter side opening of the inner dynamic pressure generating groove 81C.

[0093] Thus, the fluid can be introduced into the outer dynamic pressure generating groove 80A and the inner dynamic pressure generating groove 81C from the low pressure chamber 20 and the back pressure chamber 50, so that dynamic pressure can be reliably generated in the outer dynamic pressure generating groove 80A and the inner dynamic pressure generating groove 81C.

[0094] Further, since the sliding surface 7a overlaps with a part of the outer dynamic pressure generating groove 80A and does not overlap with the other outer dynamic pressure generating grooves 80B to 80D, it is possible to prevent generation of an undesirable dynamic pressure (negative pressure) in the outer dynamic pressure generating grooves 80B to 80D which do not overlap with the sliding surface 7a. Further, since the sliding surface 7a overlaps with a part of the inner dynamic pressure generating groove 81C and does not overlap with the other inner dynamic pressure generating grooves 81A, 81B, 81D, it is possible to prevent generation of an undesirable dynamic pressure (negative pressure) in the inner dynamic pressure generating grooves 81A, 81B, 81D which do not overlap with the sliding surface 7a.

[0095] Further, the corner portion 80e of each outer dynamic pressure generating groove 80 and the corner portion 81e of each inner dynamic pressure generating groove 81 face in opposite directions in the circumferential direction. In other words, since the corner portions 80e of the outer dynamic pressure generating grooves 80 and the corner portions 81e of the inner dynamic pressure generating grooves 81 which are adjacent in the radial direction face in opposite directions in the eccentric rotation direction of the sliding surface 7a, it is possible to generate a large dynamic pressure at the corner portions 80e of the outer dynamic pressure generating grooves 80 and the corner portions 81e of the inner dynamic pressure generating grooves 81 at positions on the sliding surface 7a which are located on both sides in the radial direction of the sliding surface 7a. Figure 5 In this state, it is possible to generate a large dynamic pressure at the corner portion 80e of the outer dynamic pressure generating groove 80A at a position on the sliding surface 8a which is located from 10 o'clock to about 2 o'clock and the corner portion 81e of the inner dynamic pressure generating groove 81C at a position on the sliding surface 8a which is located from 10 o'clock to about 2 o'clock, i.e., to generate a large dynamic pressure on both sides in the radial direction of the sliding surface 8a. Thus, it is possible to separate the sliding surfaces 7a, 8a from each other in a state in which the inclination of the sliding surfaces 7a, 8a is suppressed.

[0096] Further, since the back pressure chamber 50 extends to the inner diameter side of the sliding surfaces 7a, 8a, the fluid in the back pressure chamber 50 is introduced from the inner diameter side of the sliding surfaces 7a, 8a when the sliding surfaces 7a, 8a are separated from each other. Further, when the scroll type compression mechanism 4 is driven, the pressure of the back pressure chamber 50 becomes high, and the fluid at high pressure is introduced from the back pressure chamber 50 between the sliding surfaces 7a, 8a, so that it is possible to further separate the sliding surfaces 7a, 8a from each other by the pressure of the fluid.

[0097] Further, returning to Figure 3Since the radial separation width L5 of each external dynamic pressure generating groove 80 and each internal dynamic pressure generating groove 81 is larger than the radial width L6 of the sliding surface 7a of the side seal 7, the sliding surface 7a does not overlap with the other of the radially adjacent external dynamic pressure generating groove 80 and internal dynamic pressure generating groove 81 when it overlaps with one of the radially adjacent external dynamic pressure generating groove 80 and internal dynamic pressure generating groove 81.

[0098] For example, such as Figure 5 As shown in the enlarged view on the upper side, the sliding surface 7a, when overlapping with the external dynamic pressure generating groove 80A, does not overlap with the radially adjacent internal dynamic pressure generating groove 81A. Furthermore, as... Figure 5 As shown in the enlarged portion on the lower side, the sliding surface 7a does not overlap with the radially adjacent outer dynamic pressure generating groove 80A when it overlaps with the inner dynamic pressure generating groove 81A.

[0099] That is, the sliding surface 7a is not arranged to extend radially adjacent to the outer dynamic pressure generating groove 80A and the inner dynamic pressure generating groove 81A, so it is possible to prevent positive pressure from being generated in the outer dynamic pressure generating groove 80A and negative pressure from being generated in the inner dynamic pressure generating groove 81A at the same time, and to prevent negative pressure from being generated in the outer dynamic pressure generating groove 80C and positive pressure from being generated in the inner dynamic pressure generating groove 81C at the same time.

[0100] Furthermore, as described above, corresponding to the eccentric rotation angle of the sliding surface 7a, the positions of the outer dynamic pressure generating grooves 80A to 80D and the inner dynamic pressure generating grooves 81A to 81D that overlap with the sliding surface 7a move continuously on the sliding surface 8a. Therefore, regardless of the eccentric rotation angle of the sliding surface 7a, the sliding surfaces 7a and 8a can be separated within the entire circumference of the sliding surface 8a while suppressing the tilting of the sliding surfaces 7a and 8a.

[0101] For example, in Figure 6 In the state where the side seal 7 moves in the direction of the white arrow, a large dynamic pressure is generated at the corner 80e of the outer dynamic pressure generating groove 80C and the corner 81e of the inner dynamic pressure generating groove 81A, which can separate the sliding surfaces 7a and 8a from each other while suppressing the tilting of the sliding surfaces 7a and 8a.

[0102] In addition, Figure 5 In the middle, the opposite side seal 7 from Figure 4 The state of (a) is towards Figure 4 The form of (b) during state transition is described, in Figure 6 In the middle, for from Figure 4 The state of (c) is towards Figure 4 The morphology of (d) during its movement is described, but the side seal 7 from Figure 4 The state of (b) is towards Figure 4 The state of (c), from Figure 4The state of (d) is oriented towards Figure 4 When state (a) moves, dynamic pressure is generated in approximately the same form, so its description is omitted.

[0103] Example 2

[0104] The following is for reference Figure 7 The sliding surface 108a of the thrust plate 108 in Embodiment 2 will be described. Furthermore, repeated structural descriptions identical to those in Embodiment 1 described above will be omitted.

[0105] like Figure 7 As shown, a plurality of external dynamic pressure generating grooves 180 are provided circumferentially on the sliding surface 108a of the thrust plate 108. The external dynamic pressure generating grooves 180 and the external space on the outer diameter side (i.e., the low-pressure chamber 20, as shown in the figure) are connected. Figure 1 The sliding surface 108a is not provided with the internal dynamic pressure generating groove 81 as in Embodiment 1, and the inner diameter side of the sliding surface 108a is formed as a flat surface by the surface 182a of the land portion 182.

[0106] exist Figure 7 The image shows the side seal 7 configured near the 12 o'clock position from a position concentric with the thrust plate 108 (see reference). Figure 4 (a)

[0107] In this state, the sliding surface 7a overlaps with a plurality of external dynamic pressure generating grooves 180 (i.e., a portion of the dynamic pressure generating grooves) on the sliding surface 108a from 10 o'clock to around 2 o'clock, but does not overlap with a plurality of external dynamic pressure generating grooves 180 (i.e., other dynamic pressure generating grooves) on the sliding surface 108a from 3 o'clock to around 9 o'clock.

[0108] Therefore, when the side seal 7 moves in the direction of the white arrow, a large dynamic pressure is generated at the acute angle 180e of each external dynamic pressure generating groove 180 near the 10 o'clock to 2 o'clock position on the sliding surface 108a, while no dynamic pressure is generated at the position near the 3 o'clock to 9 o'clock position on the sliding surface 108a.

[0109] In this way, dynamic pressure can be generated only in the external dynamic pressure generating groove 180 that overlaps with the sliding surface 7a of the side seal 7, thus preventing unwanted negative pressure from being generated in other external dynamic pressure generating grooves 180 that do not overlap with the sliding surface 7a.

[0110] In addition, in this embodiment 2, a plurality of external dynamic pressure generating grooves 180 are provided circumferentially and no internal dynamic pressure generating grooves are provided. However, it is also possible to provide a plurality of internal dynamic pressure generating grooves circumferentially and no external dynamic pressure generating grooves are provided.

[0111] Example 3

[0112] Next, refer to Figure 8The sliding surface 208a of the thrust plate 208 in Embodiment 3 will be described. Furthermore, repeated structural descriptions identical to those in Embodiment 1 described above are omitted.

[0113] like Figure 8 As shown, between each external dynamic pressure generating groove 280 and each internal dynamic pressure generating groove 281 on the sliding surface 208a of the thrust plate 208, a plurality of non-connecting grooves (three in this embodiment 3) are arranged radially, and the non-connecting grooves are surrounded by the land portion 282.

[0114] Specifically, the sliding surface 208a of the thrust plate 208 has a first non-connecting groove 283 adjacent to the inner diameter side of the outer dynamic pressure generating groove 280, a second non-connecting groove 284 adjacent to the outer diameter side of the inner dynamic pressure generating groove 281, and a third non-connecting groove 285 disposed between the first non-connecting groove 283 and the second non-connecting groove 284. In this embodiment 3, the circumferential width of the outer dynamic pressure generating groove 280, the inner dynamic pressure generating groove 281, the first non-connecting groove 283, the second non-connecting groove 284, and the third non-connecting groove 285 is larger than the radial width.

[0115] The first non-connecting groove 283 is approximately parallelogram-shaped when viewed axially, and has acute corners 283a and 283b facing the counterclockwise inner diameter side and the clockwise outer diameter side. The second non-connecting groove 284 is approximately parallelogram-shaped when viewed axially, and has acute corners 284a and 284b facing the counterclockwise inner diameter side and the clockwise outer diameter side. The third non-connecting groove 285 is approximately rectangular with a long side in the circumferential direction when viewed axially.

[0116] These external dynamic pressure generating grooves 280, internal dynamic pressure generating grooves 281, first non-connecting grooves 283, and second non-connecting grooves 284 are arranged on an imaginary line extending radially from the center point of the thrust plate 208 (illustration omitted). Furthermore, the third non-connecting groove 285 is arranged slightly offset circumferentially from the radially arranged external dynamic pressure generating grooves 280, internal dynamic pressure generating grooves 281, first non-connecting grooves 283, and second non-connecting grooves 284.

[0117] exist Figure 8 The image shows the side seal 7 configured near the 12 o'clock position from a position concentric with the thrust plate 208 (see reference). Figure 4 (a)

[0118] In this state, on the sliding surface 208a, the portion from 11 o'clock to the vicinity of 1 o'clock, the sliding surface 7a overlaps with the plurality of outer dynamic pressure generating grooves 280. On the sliding surface 208a, the portion from 2 o'clock to the vicinity of 4 o'clock, the sliding surface 7a overlaps with the plurality of first non-communicating grooves 283, the plurality of second non-communicating grooves 284, and the plurality of third non-communicating grooves 285. On the sliding surface 208a, the portion from 5 o'clock to the vicinity of 7 o'clock, the sliding surface 7a overlaps with the plurality of inner dynamic pressure generating grooves 281. On the sliding surface 208a, the portion from 8 o'clock to the vicinity of 10 o'clock, the sliding surface 7a overlaps with the plurality of first non-communicating grooves 283, the plurality of second non-communicating grooves 284, and the plurality of third non-communicating grooves 285.

[0119] When the side seal 7 moves from the state of FIG. 18 to the white arrow direction, Figure 8 When the side seal 7 moves from the state of FIG. 18 to the white arrow direction, dynamic pressure is generated mainly on the portion from 11 o'clock to the vicinity of 1 o'clock and the portion from 5 o'clock to the vicinity of 7 o'clock on the sliding surface 208a by the plurality of outer dynamic pressure generating grooves 280 and the plurality of inner dynamic pressure generating grooves 281. Also, dynamic pressure can be generated on the portion from 2 o'clock to the vicinity of 4 o'clock and the portion from 8 o'clock to the vicinity of 10 o'clock on the sliding surface 208a by the plurality of first non-communicating grooves 283, the plurality of second non-communicating grooves 284, and the plurality of third non-communicating grooves 285. Thus, the inclination of the sliding surface 7a and the sliding surface 208a can be suppressed and the sliding surface 7a and the sliding surface 208a can be separated.

[0120] Further, since the side seal 7 overlaps with any of the outer dynamic pressure generating grooves 280, the inner dynamic pressure generating grooves 281, the first non-communicating grooves 283, the second non-communicating grooves 284, and the third non-communicating grooves 285 over the entire circumferential range of the sliding surface 208a, dynamic pressure can be generated over the entire circumferential range regardless of the relative position of the side seal 7 and the sliding surface 208a.

[0121] Further, since the first non-communicating grooves 283, the second non-communicating grooves 284, and the third non-communicating grooves 285 are in a state of not communicating with the outside, when the side seal 7 slides, fluid does not flow out from each non-communicating groove to the outside, and dynamic pressure can be generated reliably. Also, large dynamic pressure can be generated by the corner portions 283a, 283b and the corner portions 284a, 284b.

[0122] Further, since the shapes of the first non-communicating grooves 283, the second non-communicating grooves 284, and the third non-communicating grooves 285 are different, dynamic pressure can be changed in correspondence with the relative position of the side seal 7 and the sliding surface 208a. That is, it is easy to design so as to separate the sliding surface 7a and the sliding surface 208a appropriately with respect to the eccentric rotation movement of the side seal 7.

[0123] Example 4

[0124] Hereinafter, with reference to Figure 9The sliding surface 308a of the thrust plate 308 in Embodiment 4 will be described. Furthermore, repeated structural descriptions identical to those in Embodiment 1 described above are omitted.

[0125] like Figure 9 As shown, between each external dynamic pressure generating groove 380 and each internal dynamic pressure generating groove 381 on the sliding surface 308a of the thrust plate 308, a plurality of (three in this embodiment 2) non-connecting grooves 383 are arranged radially.

[0126] These non-connecting grooves 383 appear as approximately parallelograms of the same shape when viewed from the axial direction, with the outer dynamic pressure generating groove 380, the inner dynamic pressure generating groove 381, and each non-connecting groove 383 arranged radially.

[0127] Since the side seal 7 overlaps with any of the grooves in the outer dynamic pressure generating groove 380, the inner dynamic pressure generating groove 381, and the non-connecting groove 383 in the entire circumferential range of the sliding surface 308a, dynamic pressure can be generated in the entire circumferential range regardless of the relative position of the side seal 7 and the sliding surface 308a.

[0128] Example 5

[0129] The following is for reference Figure 10 The sliding surface 408a of the thrust plate 408 in Embodiment 5 will be described. Furthermore, repeated structural descriptions identical to those in Embodiment 1 described above are omitted.

[0130] like Figure 10 As shown, between each external dynamic pressure generating groove 480 and each internal dynamic pressure generating groove 481 on the sliding surface 408a of the thrust plate 408, a plurality of (three in this embodiment 5) non-connecting grooves 483 are arranged. These external dynamic pressure generating grooves 480, internal dynamic pressure generating grooves 481, and each non-connecting groove 483 are the shapes of various grooves in the flip embodiments 2 and 3.

[0131] These radially arranged outer dynamic pressure generating grooves 480, inner dynamic pressure generating grooves 481, and each non-connecting groove 483 are configured in a row from the outer dynamic pressure generating grooves 480 toward the inner dynamic pressure generating grooves 481 along the eccentric rotation direction of the side seal 7. In other words, the radially arranged outer dynamic pressure generating grooves 480, inner dynamic pressure generating grooves 481, and each non-connecting groove 483 are configured at an inclination relative to the circumference. That is, the circumferential dimensions of each groove are constant, and they are connected in an inclination relative to the circumference. In addition, the circumferential dimensions are not limited to being constant, and may also increase or decrease in proportion to the outer diameter.

[0132] Thus, by inverting the outer dynamic pressure generating groove 480, the inner dynamic pressure generating groove 481, and each non-communicating groove 483 of Embodiments 2 and 3, dynamic pressure can be generated corresponding to the eccentric rotation direction of the side seal 7 in the opposite direction to Embodiments 2 and 3.

[0133] Embodiment 6

[0134] Next, the sliding surface 508a of the thrust plate 508 of Embodiment 6 will be described with reference to Figure 11 The sliding surface 508a of the thrust plate 508 of Embodiment 6 will be described. In addition, the repeated structural description of the same structure as described in Embodiment 1 will be omitted.

[0135] As shown in Figure 11 On the sliding surface 508a of the thrust plate 508, a plurality of outer dynamic pressure generating grooves 580 and inner dynamic pressure generating grooves 581 are formed in the circumferential direction. The outer dynamic pressure generating grooves 580 are formed with an acute corner portion 580e at the inner diameter end in the counterclockwise direction. The inner dynamic pressure generating grooves 581 are formed with an acute corner portion 581e at the outer diameter end in the counterclockwise direction. The outer dynamic pressure generating grooves 580 communicate with the outer space on the outer diameter side (i.e., the low pressure chamber 20 (see Figure 1 )), and the inner dynamic pressure generating grooves 581 communicate with the outer space on the inner diameter side (i.e., the back pressure chamber 50 (see Figure 1 )).

[0136] Further, between the outer dynamic pressure generating grooves 580 and the inner dynamic pressure generating grooves 581 adjacent in the radial direction on the sliding surface 508a, a first non-communicating groove 583, a second non-communicating groove 584, and a third non-communicating groove 585 are formed.

[0137] The first non-communicating groove 583 adjacent to the inner diameter side of the outer dynamic pressure generating groove 580 is substantially a parallelogram having acute corner portions 583a, 583b on the inner diameter side in the counterclockwise direction and the outer diameter side in the clockwise direction.

[0138] Further, the second non-communicating groove 584 adjacent to the outer diameter side of the inner dynamic pressure generating groove 581 is substantially a parallelogram having acute corner portions 584a, 584b on the outer diameter side in the counterclockwise direction and the inner diameter side in the clockwise direction. In addition, the third non-communicating groove 585 is substantially a long rectangle having long sides in the circumferential direction when viewed from the axial direction.

[0139] In addition, the first non-communicating groove 583 is disposed on the outer diameter side of the third non-communicating groove 585 in a manner offset in the clockwise direction from the third non-communicating groove 585, and the outer dynamic pressure generating groove 580 is disposed on the outer diameter side of the first non-communicating groove 583 in a manner offset in the clockwise direction from the first non-communicating groove 583. That is, the center lines between the circumferential directions of each groove are offset in the circumferential direction, that is, the center lines between the groves adjacent in the radial direction are discontinuous.

[0140] Furthermore, the second non-connecting groove 584 is disposed on the inner diameter side of the third non-connecting groove 585 in a clockwise direction offset from the third non-connecting groove 585, and the external dynamic pressure generating groove 580 is disposed on the inner diameter side of the first non-connecting groove 583 in a clockwise direction offset from the first non-connecting groove 583. That is, the center lines of each groove are offset circumferentially, meaning that the center lines of adjacent grooves are discontinuous in the radial direction.

[0141] exist Figure 11 In the specified state, on the sliding surface 508a, from approximately 11 o'clock to 1 o'clock, the sliding surface 7a overlaps with multiple external dynamic pressure generating grooves 580. On the sliding surface 508a, from approximately 2 o'clock to 4 o'clock, the sliding surface 7a overlaps with multiple first non-connecting grooves 583, second non-connecting grooves 584, and third non-connecting grooves 585. On the sliding surface 508a, from approximately 5 o'clock to 7 o'clock, the sliding surface 7a overlaps with multiple internal dynamic pressure generating grooves 581. On the sliding surface 508a, from approximately 8 o'clock to 10 o'clock, the sliding surface 7a overlaps with multiple first non-connecting grooves 583, second non-connecting grooves 584, and third non-connecting grooves 585.

[0142] When the side seal 7 is from Figure 11 When the state moves in the direction of the white arrow, dynamic pressure is generated on the sliding surface 508a from the 8 o'clock position to the 4 o'clock position through multiple external dynamic pressure generating grooves 580 and multiple first non-connecting grooves 583, second non-connecting grooves 584 and third non-connecting grooves 585.

[0143] On the other hand, at the location near the 7 o'clock position on the sliding surface 508a, the multiple internal dynamic pressure generating grooves 581 hardly generate dynamic pressure, and negative pressure is generated at the location near the 5 o'clock to 6 o'clock position on the sliding surface 508a.

[0144] In this way, dynamic pressure can be generated in most of the circumferential direction of the sliding surface 508a to improve the lubricity between the sliding surfaces 7a and 508a, and negative pressure can be generated in a part of the circumferential direction of the sliding surface 508a to bring the sliding surfaces 7a and 508a closer to each other, thereby maintaining the state of relative sliding between the sliding surfaces 7a and 508a.

[0145] Example 7

[0146] Next, refer to Figure 12 The sliding surface 608a of the thrust plate 608 in Embodiment 7 will be described. Furthermore, repeated structural descriptions identical to those in Embodiment 1 described above are omitted.

[0147] like Figure 12 As shown, the inner dynamic pressure generating groove 681 of the sliding surface 608a of the thrust plate 608 is connected to the land portion 682 by the outer space on the inner diameter side (i.e., the back pressure chamber 50 (see reference)). Figure 1The outer dynamic pressure generating grooves 780 are divided by the land portions 782 in a state of not communicating with the outer space on the outer diameter side, i.e., the low pressure chamber 20 (refer to FIG. 1). Further, the inner dynamic pressure generating grooves 781 communicate with the outer space on the inner diameter side, i.e., the back pressure chamber 50 (refer to FIG. 1).

[0148] Thus, dynamic pressure can be generated over the entire circumferential range of the sliding surface 608a, and therefore the sliding surfaces 7a, 608a can be separated in a state of small relative inclination of the sliding surfaces 7a, 608a.

[0149] Example 8

[0150] Next, the sliding surface 708a of the thrust plate 708 of Example 8 will be described with reference to FIG. 8. Figure 13 The sliding surface 708a of the thrust plate 708 will be described. Further, the repeated description of the structure common to that of Example 1 will be omitted.

[0151] As shown in FIG. 8, each of the outer dynamic pressure generating grooves 780 on the sliding surface 708a of the thrust plate 708 is divided by the land portion 782 in a state of not communicating with the outer space on the outer diameter side, i.e., the low pressure chamber 20 (refer to FIG. 1). Figure 13 Further, each of the inner dynamic pressure generating grooves 781 communicates with the outer space on the inner diameter side, i.e., the back pressure chamber 50 (refer to FIG. 1). Figure 1 Figure 1

[0152] Further, the first non-communicating groove 783, the second non-communicating groove 784, and the third non-communicating groove 785 are arranged between each of the outer dynamic pressure generating grooves 780 and each of the inner dynamic pressure generating grooves 781. These outer dynamic pressure generating grooves 780, inner dynamic pressure generating grooves 781, first non-communicating groove 783, second non-communicating groove 784, and third non-communicating groove 785 are in shapes of the various grooves of the reversed Examples 6 and 7.

[0153] Thus, by forming the outer dynamic pressure generating grooves 780, inner dynamic pressure generating grooves 781, first non-communicating groove 783, second non-communicating groove 784, and third non-communicating groove 785 by reversing Examples 6 and 7, dynamic pressure can be generated corresponding to the eccentric rotation direction of the side seal 7 in the opposite direction to that of Examples 6 and 7.

[0154] Further, since the outer dynamic pressure generating grooves 780 are divided by the land portions 782 in a state of not communicating with the outer space on the outer diameter side, dynamic pressure can be reliably generated when sliding against the side seal 7.

[0155] Further, in the case where the side seal 7 is eccentrically rotated in the opposite direction to that of Figure 13 Thus, dynamic pressure can be generated over the entire circumferential range of the sliding surface 708a, and therefore the sliding surfaces 7a, 708a can be separated in a state of small relative inclination of the sliding surfaces 7a, 708a.

[0156] ​​The above-described embodiments of the present application have been described with reference to the drawings, but the specific configuration is not limited to these embodiments, and modifications and additions within the scope of the gist of the present application are also included in the present application.

[0157] In the above-described embodiments 1 to 8, the side seal 7 as the sliding member is applied to the scroll compressor C used in the air conditioning system of an automobile or the like, but is not limited thereto, and can be applied to, for example, a scroll expander-compressor having an expander and a compressor integrally, or the like, as long as it is a rotary machine including an eccentric mechanism.

[0158] Further, the fluid present in the inner and outer spaces of the sliding surface of the sliding member can be any one of a gas, a liquid, or a mixed state of a gas and a liquid.

[0159] Further, the sliding member of the present application can be used in an environment in which the pressure is the same in the inner and outer sides of the sliding surface, as long as it has a sliding surface that slides in relation to the eccentric rotation, and is not limited to an environment in which there is a pressure difference in the inner and outer sides of the sliding surface. Further, the function as a seal is not essential for the sliding member of the present application, and it is sufficient that it can stably reduce the frictional resistance of the sliding surface.

[0160] Further, in the above-described embodiments 1 to 8, the case in which the side seal having the sliding surface that slides in relation has a resin structure and the thrust plate has a metal structure is described, but the material of the sliding member can be freely selected according to the use environment or the like.

[0161] Further, in the above-described embodiments 1 to 8, the case in which the dynamic pressure generation groove is formed in the sliding region of the sliding surface of the thrust plate (refer to Figure 4 ) is described, but is not limited thereto, and the dynamic pressure generation groove can be formed in the sliding surface of the side seal as the sliding member having the sliding surface that slides in relation to the eccentric rotation. Further, the dynamic pressure generation groove can be formed in both the sliding surface of the side seal and the sliding surface of the thrust plate.

[0162] Further, in the above-described embodiments 1 to 8, the structure in which the sliding surface of the side seal and the sliding surface of the thrust plate as the sliding member slide in relation to the eccentric rotation is described, but is not limited thereto, and it can be that only either one of the side seal and the thrust plate has the dynamic pressure generation groove formed in the sliding surface that slides in relation to the eccentric rotation. For example, in the case in which only the thrust plate is provided, the dynamic pressure generation groove can be formed in either one or both of the sliding surface of the thrust plate as the sliding member and the back surface of the end plate of the movable scroll. Further, in the case in which only the side seal is provided, the dynamic pressure generation groove can be formed in the sliding surface of the side seal as the sliding member. In this case, the side seal also functions as a thrust bearing that abuts against the inner peripheral surface of the inner case to receive the axial load of the movable scroll.

[0163] In addition, in a case where the back surface of the end plate of the movable scroll abuts against the inner peripheral surface of the inner case to function as a thrust bearing that receives the axial load of the movable scroll without the side seal and the thrust plate, the dynamic pressure generation groove can be formed on the sliding surface of the back surface of the end plate of the movable scroll or the inner case.

[0164] In addition, the above-described embodiments 1 to 8 illustrate a manner in which the low-pressure-side outer space exists on the outer diameter side of the side seal and the high-pressure outer space exists on the inner diameter side of the side seal, but a manner in which the low-pressure-side outer space exists on the inner diameter side of the side seal and the high-pressure outer space exists on the outer diameter side of the side seal can also be adopted.

[0165] In addition, in the above-described embodiments 1 to 8, the tapering portion of the outer dynamic pressure generation groove and the inner dynamic pressure generation groove is exemplified by an angular portion that is an acute angle, but is not limited thereto, and can be a face or a curved surface that is perpendicular to the eccentric rotation direction as long as the tip of the dynamic pressure generation groove is tapered toward the eccentric rotation direction.

[0166] In addition, in the above-described embodiments 1 to 8, a manner in which the opposed sliding surface relatively slides with respect to the sliding surface in a manner in which the one outer dynamic pressure generation groove and the inner dynamic pressure generation groove do not overlap with the other outer dynamic pressure generation groove and the inner dynamic pressure generation groove when overlapping is exemplified, but a manner in which the opposed sliding surface relatively slides in a manner in which the opposed sliding surface always overlaps with each of the outer dynamic pressure generation groove and the inner dynamic pressure generation groove can also be adopted.

[0167] In addition, in the above-described embodiments 1 to 8, a manner in which the side wall of the outer dynamic pressure generation groove and the side wall of the inner dynamic pressure generation groove are curved is exemplified, but can be formed in a straight line.

[0168] In addition, the number of the outer dynamic pressure generation grooves and the inner dynamic pressure generation grooves is not limited to the above-described embodiments 1 to 8, and can be freely changed. In addition, in the above-described embodiments 1, 3 to 8, a manner in which the same number of the outer dynamic pressure generation grooves and the inner dynamic pressure generation grooves are provided is exemplified, but is not limited thereto, and different numbers thereof can also be provided.

[0169] In addition, in the above-described embodiments 1, 3 to 8, a case in which the outer dynamic pressure generation groove is the dynamic pressure generation groove and the inner dynamic pressure generation groove is the other dynamic pressure generation groove is exemplified, but a case in which the inner dynamic pressure generation groove is the dynamic pressure generation groove and the outer dynamic pressure generation groove is the other dynamic pressure generation groove can also be adopted.

[0170] Label Explanation

[0171] 4: scroll compression mechanism; 7: side seal; 7a: sliding surface (opposite sliding surface); 8: thrust plate (sliding member); 8a: sliding surface; 20: low-pressure chamber (outer space on the outer diameter side); 41: fixed scroll; 42: movable scroll; 50: back-pressure chamber (outer space on the inner diameter side); 80, 80A-80B: outer dynamic pressure generating groove (dynamic pressure generating groove); 80e: corner portion; 81, 81A-81B: inner dynamic pressure generating groove (another dynamic pressure generating groove); 81e: corner portion; 82: land portion; 108: thrust plate (sliding member); 108a: sliding surface; 180: outer dynamic pressure generating groove (dynamic pressure generating groove); 180e: corner portion; 208: thrust plate (sliding member); 208a: sliding surface; 280: outer dynamic pressure generating groove (dynamic pressure generating groove); 281: inner dynamic pressure generating groove (another dynamic pressure generating groove); 283: first non-communicating groove; 284: second non-communicating groove; 285: third non-communicating groove; 308: thrust plate (sliding member); 308a: sliding surface; 380: outer dynamic pressure generating groove (dynamic pressure generating groove); 381: inner dynamic pressure generating groove (another dynamic pressure generating groove); 383: non-communicating groove; 408: thrust plate (sliding member); 408a: sliding surface; 480: outer dynamic pressure generating groove (dynamic pressure generating groove); 481: inner dynamic pressure generating groove (another dynamic pressure generating groove); 483: non-communicating groove; 508: thrust plate (sliding member); 508a: sliding surface; 580: outer dynamic pressure generating groove (dynamic pressure generating groove); 580e: corner portion; 581: inner dynamic pressure generating groove (another dynamic pressure generating groove); 581e: corner portion; 583: first non-communicating groove; 584: second non-communicating groove; 585: third non-communicating groove; 608: thrust plate (sliding member); 608a: sliding surface; 681: inner dynamic pressure generating groove (another dynamic pressure generating groove); 682: land portion; 708: thrust plate (sliding member); 708a: sliding surface; 780: outer dynamic pressure generating groove (dynamic pressure generating groove); 781: inner dynamic pressure generating groove (another dynamic pressure generating groove); 783: first non-communicating groove; 784: second non-communicating groove; 785: third non-communicating groove; C: scroll compressor; M: drive motor.

Claims

1. A sliding component having a sliding surface that slides relative to each other during eccentric rotation, wherein, At least one of the inner diameter side and the outer diameter side of the sliding surface is provided with a plurality of dynamic pressure generating grooves in the circumferential direction. The dynamic pressure generating grooves extend in a manner that gradually tapers at the front end towards the downstream side of the opposite eccentric rotation direction relative to the opposing sliding surface. At least one of the inner diameter side and the outer diameter side of the sliding surface is provided with a plurality of additional dynamic pressure generating grooves along the circumferential direction. These additional dynamic pressure generating grooves extend in a manner that gradually tapers at their front ends toward the downstream side relative to the opposing sliding surface in the opposite eccentric rotation direction. The sliding surface and the opposing sliding surface slide relative to each other with eccentric rotation, such that the opposing sliding surface overlaps with a portion of the plurality of dynamic pressure generating grooves and does not overlap with other dynamic pressure generating grooves, and the opposing sliding surface overlaps with a portion of the plurality of other dynamic pressure generating grooves and does not overlap with other other dynamic pressure generating grooves.

2. The sliding component according to claim 1, wherein, The downstream end of the eccentric rotation direction of the dynamic pressure generating groove is an acute angle.

3. The sliding component according to claim 1 or 2, wherein, The dynamic pressure generating groove is connected to the external space of the sliding surface.

4. The sliding component according to claim 1, wherein, The taper of the radially adjacent dynamic pressure generating groove and the taper of the other dynamic pressure generating groove are formed to face opposite directions in the eccentric rotation direction.

5. The sliding component according to claim 1, wherein, The dynamic pressure generating groove and the other dynamic pressure generating groove are radially separated, and the separation width is greater than the radial width of the annular opposing sliding surface that slides relative to the sliding surface.

6. The sliding component according to claim 1, wherein, A plurality of non-connecting slots are provided circumferentially between the dynamic pressure generating slot and the other dynamic pressure generating slot, and the non-connecting slots are surrounded by landmasses that separate the dynamic pressure generating slots from the other dynamic pressure generating slots.

7. The sliding member according to claim 6, wherein, The non-connected slots are arranged radially between the radially adjacent dynamic pressure generating slots and the other dynamic pressure generating slots, and each non-connected slot has a different shape.

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