sliding parts

Abstract

The present invention provides a sliding component capable of reducing the frictional resistance of a sliding surface that is eccentrically rotated. A sliding component (7) is annular in shape and has a sliding surface (7a) that slides relative to each other with eccentric rotation. On the sliding surface (7a), a plurality of grooves (70) opening into a fluid-containing space (50) on the inner diameter side are provided in the circumferential direction. The grooves (70) are formed by connecting a first wall surface (70a) extending circumferentially along the sliding surface (7a) and a second wall surface (70c, 70c) extending radially.

Description

Technical Field

[0001] The present invention relates to a sliding component for rotating machinery including an eccentric mechanism. Background Technology

[0002] Conventionally, rotating machinery including an eccentric mechanism, such as a scroll compressor for an automotive air conditioning system, has the following mechanism: it includes a scroll compression mechanism and an eccentric mechanism. The scroll compression mechanism consists of a fixed scroll disk with scroll-shaped volutes on the surface of the end plate and a movable scroll disk with scroll-shaped volutes on the surface of the end plate. The eccentric mechanism causes the rotating shaft to rotate eccentrically. The rotation of the rotating shaft causes the movable scroll disk to slide relative to the fixed scroll disk as it rotates eccentrically. This pressurizes the refrigerant supplied from the low-pressure chamber on the outer diameter side of the two scroll disks, and the high-pressure refrigerant is discharged from the discharge hole formed in the center of the fixed scroll disk (see Patent Document 1).

[0003] Furthermore, the scroll compressor shown in Patent Document 1 includes a back pressure supply mechanism that supplies a portion of the refrigerant compressed by the scroll compressor to a back pressure chamber, which is formed on the back side of a thrust plate that bears the axial load of the movable scroll. Through the back pressure acting on the back side of the movable scroll, the movable scroll is pressed towards the fixed scroll. This reduces axial refrigerant leakage between the two scrolls and improves the compression efficiency of the scroll compressor.

[0004] Existing technical documents

[0005] Patent documents

[0006] Patent Document 1: Japanese Patent Application Publication No. 2016-61208 (Pages 5-6) Figure 1 ) Summary of the Invention

[0007] The problem that the invention aims to solve

[0008] In the scroll compressor shown in Patent Document 1, by inserting a sealing ring between the thrust plate and the housing, the thrust plate can be moved axially while preventing back pressure leakage from the back pressure chamber. This allows the movable scroll plate to be pressed towards the fixed scroll plate via the thrust plate. However, the sliding surface of the thrust plate is pressed against the back of the movable scroll plate, resulting in high frictional resistance on the sliding surface, which may affect the operation of the movable scroll plate.

[0009] This invention was made in view of such a problem, and its purpose is to provide a sliding component that can reduce the frictional resistance of the sliding surface that is accompanied by eccentric rotation.

[0010] Methods for solving problems

[0011] To address the aforementioned issues, the sliding component of the present invention...

[0012] It is annular in shape and has a sliding surface that slides relative to each other as it rotates eccentrically.

[0013] On the sliding surface, a plurality of grooves are provided circumferentially, each having an opening to at least one of the inner diameter side and the outer diameter side, allowing fluid to pass through.

[0014] The groove is formed by connecting a first wall extending circumferentially along the sliding surface and a second wall extending radially.

[0015] Thus, fluid can flow into the sliding surfaces from the opening of the groove provided on the sliding surfaces that slide relative to each other with eccentric rotation, and can generate dynamic pressure by colliding with the first and second walls in accordance with the radial and circumferential components of the relative movement of the groove with eccentric rotation. Therefore, the sliding surfaces can be slightly separated from each other and form a fluid film, thereby improving the lubricity between the sliding surfaces and reducing the frictional resistance of the sliding surfaces.

[0016] Alternatively, the corners of the first and second walls of the groove may have sharp angles.

[0017] This allows fluid moving along the first and second walls within the groove to flow from the apex and vicinity of the corner towards the sliding surface, thus generating high dynamic pressure at the corner.

[0018] Alternatively, the first wall surface can be an arc surface with a center at the center of the sliding surface, and the second wall surface can be a radial surface extending from the center of the sliding surface.

[0019] As a result, the radial component of the relative movement of the groove, which is accompanied by eccentric rotation, collides with the first wall, and the circumferential component collides with the second wall, thus easily generating dynamic pressure through their respective walls.

[0020] Alternatively, the groove may be a groove that is longer in the circumferential direction.

[0021] Therefore, the fluid can easily flow from the opening of the groove into the sliding surface, and even when the radial component of the relative movement of the groove accompanied by eccentric rotation does not act on the first wall, the fluid in the groove can collide with the second wall through the circumferential component to generate high dynamic pressure.

[0022] Alternatively, the groove may have an opening in the space on the inner diameter side.

[0023] As a result, the fluid flowing into the tank from the opening is easily retained in the tank due to centrifugal force.

[0024] Alternatively, the groove may have an opening towards the high-pressure side.

[0025] Therefore, due to the pressure of the fluid, the fluid can easily flow into the tank from the opening, thus generating higher dynamic pressure.

[0026] Alternatively, the sliding component may be the narrower sliding component in a pair of sliding components that slide relative to each other.

[0027] Therefore, dynamic pressure can be reliably generated between the sliding surfaces that slide relative to each other during eccentric rotation. Attached Figure Description

[0028] Figure 1 This is a schematic diagram showing the structure of a scroll compressor that incorporates a side seal, which is an embodiment of the present invention, as an example of a sliding component.

[0029] Figure 2 This is a diagram illustrating the sliding surface of the side seal according to an embodiment of the present invention;

[0030] Figure 3 This diagram illustrates the relative sliding of the sliding surface of the side seal and the sliding surface of the thrust plate according to an embodiment of the present invention. Furthermore, it shows the positional relationship between the sliding surface of the side seal and the sliding surface of the thrust plate when the rotation axis is eccentrically rotated to (b) 90 degrees, (c) 180 degrees, and (d) 270 degrees, starting from position (a).

[0031] Figure 4 (a) is shown in Figure 3 (c) is a magnified view of the pressure distribution within region A of the sliding surface of the side seal, caused by the relative movement of the grooves due to the eccentric rotation of the rotating shaft, resulting in pressure within multiple grooves. Figure 4 (b) is shown in Figure 3 (c) is a magnified view of the distribution of pressure generated in multiple grooves in region B of the sliding surface of the side seal due to the relative movement of the grooves accompanying the eccentric rotation of the rotating shaft.

[0032] Figure 5 This is a diagram showing a modified example 1 of a groove formed on the sliding surface of the side seal;

[0033] Figure 6 This is a diagram showing a modified example 2 of a groove formed on the sliding surface of the side seal;

[0034] Figure 7 Figures 3 to 5 show variations of the groove formed on the sliding surface of the side seal. Detailed Implementation

[0035] Hereinafter, the method of implementing the sliding component of the present invention will be described based on embodiments.

[0036] Example

[0037] Reference Figures 1 to 4 The sliding component of the embodiment will be described. For ease of explanation, dots are added to the grooves or the like formed on the sliding surface of the sliding component in the accompanying drawings.

[0038] The sliding component of the present invention is applied to a scroll compressor C used in air conditioning systems of rotating machinery including an eccentric mechanism, such as automobiles, for drawing in, compressing, and discharging a refrigerant as a fluid. Furthermore, in this embodiment, the refrigerant is a gas mixed with a mist of lubricating oil.

[0039] First, let's explain the scroll compressor C. For example... Figure 1 As shown, the scroll compressor C mainly consists of a housing 1, a rotating shaft 2, an inner shell 3, a scroll compression mechanism 4, a side seal 7 as a sliding component, a thrust plate 8, and a drive motor M.

[0040] The housing 1 consists of a cylindrical outer shell 11 and a cover 12 that closes one opening of the outer shell 11. Inside the outer shell 11 are formed: a low-pressure chamber 20, into which low-pressure refrigerant is supplied through a refrigerant circuit (not shown) via a suction port 10; a high-pressure chamber 30 into which high-pressure refrigerant, compressed by the scroll compressor 4, is discharged; and a back-pressure chamber 50 into which a portion of the refrigerant compressed by the scroll compressor 4, along with lubricating oil, is supplied. Furthermore, the back-pressure chamber 50 is formed inside a cylindrical inner shell 3 housed within the outer shell 11.

[0041] A discharge passage 13, connecting a refrigerant circuit (not shown) to the high-pressure chamber 30, is formed on the cover 12. Additionally, a portion of a back pressure passage 14, branching from the discharge passage 13, connecting the high-pressure chamber 30 to the back pressure chamber 50, is formed on the cover 12. Furthermore, an oil separator 6 for separating lubricating oil from the refrigerant is provided on the discharge passage 13.

[0042] The inner shell 3 is fixed with one end abutting against the end plate 41a of the fixed scroll disk 41 constituting the scroll compressor mechanism 4. Furthermore, a radially penetrating suction passage 15 is formed at one end of the inner shell 3. That is, the low-pressure chamber 20 extends from the outside of the inner shell 3 into the interior of the inner shell 3 via the suction passage 15. Refrigerant supplied to the interior of the inner shell 3 through the suction passage 15 is drawn into the scroll compressor mechanism 4.

[0043] The scroll compression mechanism 4 mainly consists of the following parts: a fixed scroll plate 41, which is fixed relative to the cover 12 in a generally sealed manner; and a movable scroll plate 42, which is housed inside the inner shell 3.

[0044] The fixed scroll plate 41 is made of metal and has a scroll-shaped vortex 41b protruding from the surface of the circular end plate 41a, i.e., one end face of the end plate 41a. In addition, a recess 41c is formed on the fixed scroll plate 41 that is recessed toward the back side of the end plate 41a, i.e., the inner diameter side of the other end face of the end plate 41a. The high-pressure chamber 30 is defined by the recess 41c and the end face of the cover 12.

[0045] The movable scroll plate 42 is made of metal and has a scroll-shaped vortex 42b protruding from the surface of the circular end plate 42a, i.e., one end face of the end plate 42a. Additionally, a protrusion 42c is formed on the movable scroll plate 42, protruding from the center of the back side of the end plate 42a, i.e., the other end face of the end plate 42a. An eccentric portion 2a formed at one end of the rotating shaft 2 is rotatably inserted into the protrusion 42c. Furthermore, in this embodiment, the eccentric portion 2a of the rotating shaft 2 and the counterweight portion 2b protruding outwards from one end of the rotating shaft 2 constitute an eccentric mechanism for eccentrically rotating the rotating shaft 2.

[0046] When the rotating shaft 2 is driven by the drive motor M, the eccentric part 2a rotates eccentrically, and the movable scroll plate 42 slides relative to the fixed scroll plate 41 along with the eccentric rotation. At this time, the movable scroll plate 42 rotates eccentrically relative to the fixed scroll plate 41. With this rotation, the contact position of the scroll rings 41b and 42b moves sequentially in the direction of rotation, and the compression chamber 40 formed between the scroll rings 41b and 42b gradually shrinks while moving towards the center. As a result, the refrigerant drawn 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 discharged into the high-pressure chamber 30 through the discharge hole 41d provided in the center of the fixed scroll plate 41.

[0047] Next, the side seal 7, which serves as a sliding component in this embodiment, will be described. For example... Figure 1 and Figure 2 As shown, the side seal 7 is made of resin, has a rectangular cross-section, and appears as an annular shape when viewed axially. It is fixed to the back of the end plate 42a of the movable scroll plate 42. A sliding surface 7a is formed on one side of the side seal 7, which abuts against the sliding surface 8a of the thrust plate 8.

[0048] like Figure 2 As shown, a plurality of spaces on the inner diameter side, i.e., grooves 70 opening toward the back pressure chamber 50, are arranged at equal intervals along the circumferential direction on the sliding surface 7a of the side seal 7. Furthermore, the number of grooves 70 is not limited, but in order to obtain the dynamic pressure generation effect of the second wall surfaces 70c, 70c described later, it is preferable to have more than 10.

[0049] The groove 70 is formed as a rectangular groove with a circumferential dimension L1 larger than the radial dimension L2 (L1 > L2). In detail, the groove 70 is composed of the following parts: a first wall surface 70a, which is an arc surface extending axially orthogonal to the flat sliding surface 7a and having a center at the center Q of the sliding surface 7a; second wall surfaces 70c, 70c, which are radial surfaces extending axially orthogonal to the sliding surface 7a and extending from the center Q of the sliding surface 7a; and a planar bottom surface 70b, which extends parallel to the sliding surface 7a.

[0050] Furthermore, the two circumferential ends of the first wall surface 70a of the groove 70 are connected approximately orthogonally to the outer diameter ends of the second wall surfaces 70c and 70c, and have corner portions 70d and 70d. That is, the groove 70 is composed of wall surfaces with angles, including the first wall surface 70a and the second wall surfaces 70c and 70c.

[0051] Furthermore, the bottom surface 70b of the groove 70 is not limited to being formed as a planar shape extending parallel to the sliding surface 7a; for example, it can also be formed as an inclined surface or a curved surface.

[0052] Furthermore, the circumferential dimension L1 of the groove 70 is larger than the circumferential dimension L3 of the boss portion between adjacent grooves 70 (L1 > L3). That is, multiple grooves 70 are densely formed throughout the entire circumference of the sliding surface 7a, and the opening area of ​​the grooves 70 that allow fluid to flow in from the space on the inner diameter side of the sliding surface 7a becomes larger.

[0053] In addition, the groove 70 is formed as a rectangular groove with a circumferential dimension L1 larger than the radial dimension L2 (L1 > L2), which is used to maintain a larger fluid capacity within the groove 70.

[0054] like Figure 1 As shown, the thrust plate 8 is made of metal and is annular in shape. A sealing ring 43 is fixed to one end face of the thrust plate 8, which abuts against the inner circumferential surface of the inner shell 3. Thus, the thrust plate 8 functions as a thrust bearing that bears the axial load of the movable scroll plate 42 via the side seal 7.

[0055] 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 sealed to the rotating shaft 2 inserted through the through hole 3a by a sealing ring 44 fixed to the inner circumference of the through hole 3a located at the center of the other end of the inner shell 3, thus forming a sealed space. In addition, a throttling orifice (not shown) is provided on the back-pressure communication path 14, which spans the cover 12, the fixed scroll plate 41, and the inner shell 3 and connects the high-pressure chamber 30 and the back-pressure chamber 50. The refrigerant in the high-pressure chamber 30, after being depressurized and adjusted by the throttling orifice, 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. Additionally, a pressure relief hole 16 is formed on the inner shell 3, which extends radially and connects the low-pressure chamber 20 and the back-pressure chamber 50. A pressure regulating valve 45 is installed in the pressure relief hole 16. The pressure regulating valve 45 opens when the pressure in the back-pressure chamber 50 exceeds a set value.

[0056] Furthermore, a protrusion 42c of a movable scroll plate 42 is inserted into a through hole 8b in the center of the thrust plate 8. The through hole 8b is formed to allow eccentric rotation by the eccentric portion 2a of the rotating shaft 2, which is 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 as the rotating shaft 2 rotates eccentrically (see reference). Figure 3 ).

[0057] In addition, Figure 3 middle, Figure 3 (a) to (d) show the movement from the fixed scroll plate 41 (refer to) Figure 1 In the rotation trajectory of protrusion 42c under the condition of side observation, protrusion 42c is... Figure 3 (a) The reference points were rotated 90 degrees, 180 degrees, and 270 degrees clockwise, respectively. 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 using dots. For ease of explanation, only the eccentric portion 2a inserted into the protrusion 42c is shown regarding the rotating shaft 2; the balancing counterweight 2b and other components constituting the eccentric mechanism are omitted.

[0058] Thus, the side seal 7 is a sliding component having a sliding surface 7a that slides relative to the sliding surface 8a of the thrust plate 8 with eccentric rotation. On the sliding surface 7a of the side seal 7, a plurality of grooves 70 are provided circumferentially, each opening to a back pressure chamber 50 containing fluid towards its inner diameter. The grooves 70 are formed by connecting a first wall surface 70a extending circumferentially along the sliding surface 7a and second wall surfaces 70c, 70c extending radially. Therefore, fluid can flow from the openings of the grooves 70 on the sliding surface 7a, which slides relative to each other with eccentric rotation, into the space between the sliding surfaces 7a and 8a, and can move in response to the relative movement of the grooves 70 with eccentric rotation (see reference). Figure 3 The radial and circumferential components of the fluid cause the fluid to collide with the first wall surface 70a and the second wall surfaces 70c, 70c, generating dynamic pressure. Therefore, by slightly separating the sliding surfaces 7a and 8a from each other and forming a liquid film of lubricating oil, the lubricity between the sliding surfaces 7a and 8a can be improved, and the frictional resistance of the sliding surface 7a can be reduced.

[0059] Furthermore, multiple grooves 70 are provided circumferentially along the sliding surface 7a, thus dynamic pressure can be generated through the multiple grooves 70 in response to the relative movement of the grooves 70 accompanying eccentric rotation. Additionally, the distribution of pressure generated within the multiple grooves 70 due to the relative movement of the grooves 70 accompanying the eccentric rotation of the rotating shaft 2 (see reference). Figure 4 It moves approximately circumferentially with eccentric rotation. Therefore, fluid flowing from the upstream circumferential groove 70 to the sliding surfaces 7a and 8a, accompanied by dynamic pressure, easily flows into the adjacent downstream circumferential groove 70, easily forming a lubricating oil film throughout the entire circumferential direction between the sliding surfaces 7a and 8a. Furthermore, in Figure 4 In the diagram, the area enclosed by the dashed lines shown on the first wall surface 70a or the second wall surface 70c of each groove 70 represents the area in which pressure is generated within each groove 70.

[0060] Furthermore, through the relative movement of the grooves 70 accompanied by eccentric rotation, the fluid within the grooves 70 collides with the first wall surface 70a, the second wall surface 70c, or both walls 70a and 70c. This causes the fluid to flow between the sliding surfaces 7a and 8a, generating dynamic pressure. However, within each groove 70, the position with the highest pressure corresponds to... Figure 3 The pressure varies with the rotation angle of the protrusion 42c shown. That is, the position of the highest pressure in each groove 70 is different depending on the rotation angle of the protrusion 42c. However, by arranging multiple grooves 70 at equal intervals along the circumference of the sliding surface 7a, the deviation of the dynamic pressure generated in the circumference between the sliding surfaces 7a and 8a can be suppressed.

[0061] Furthermore, the groove 70 is connected to the first wall surface 70a and the second wall surfaces 70c, 70c to form corner portions 70d, 70d with sharp edges. Thus, as... Figure 2As shown in the enlarged portion, fluid (illustrated by white arrows) moving along the first wall 70a and the second wall 70c, 70c within the groove 70 can flow out from the apex and vicinity of the corners 70d, 70d to the sliding surfaces 7a, 8a, thus generating high dynamic pressure at the corners 70d, 70d.

[0062] Furthermore, the first wall surface 70a is at the center Q of the sliding surface 7a (refer to...). Figure 2 The first wall 70a has a central arc surface, and the second wall 70c is a radial surface extending from the center Q of the sliding surface 7a. Thus, the flow of fluid in the groove 70 during the relative movement of the groove 70 with its eccentric rotation consists of radial and circumferential components. The radial component collides with the first wall 70a, and the circumferential component collides with the second wall 70c, thus easily generating dynamic pressure on each wall 70a and 70c.

[0063] The following is about... Figure 3 (c) A summary of the fluid flow, etc., within the tank 70 under the condition of [condition], for configuration in [location]. Figure 2 Let's take the slot 70 on the top, right, bottom, and left as an example for explanation.

[0064] The slot 70 configured above will be described. Slots 70 in which the radial component of the movement per unit time of the slot 70, accompanying eccentric rotation, is more prominent in the direction approaching the center Q, for example... Figure 4 In the groove 70 at part (a), since the groove 70 is formed to be relatively long in the circumferential direction, the pressure-bearing area of ​​the first wall surface 70a in the radial component of the relative movement of the groove 70 with respect to the eccentric rotation is large. As a result, the fluid in the groove 70 easily collides with the first wall surface 70a and generates dynamic pressure. In addition, the fluid easily flows in from the opening of the groove 70, and the fluid flowing into the groove 70 easily collides with the first wall surface 70a and flows out between the sliding surfaces 7a and 8a.

[0065] Next, the slot 70 located on the right will be described. Slots 70 with a larger component of clockwise rotation around center Q, where the movement per unit time of slot 70 is accompanied by eccentric rotation, are, for example... Figure 4 In the groove 70 at part (b), the first wall 70a extends parallel to the circumferential component of the rotation direction in the relative movement of the groove 70 with eccentric rotation. Therefore, the fluid in the groove 70 can easily move along the first wall 70a and collide with the second wall 70c, which can easily generate dynamic pressure.

[0066] Next, the slot 70 configured below will be described. Slots 70 in which the radial component of the movement per unit time of the slot 70 is more significant in the direction away from the center Q due to eccentric rotation, for example, in... Figure 2The fluid is disposed in the lower groove 70, and the fluid in the groove 70 can easily flow out from the opening of the groove 70 to the space on the inner diameter side between the sliding surfaces 7a and 8a, with almost no dynamic pressure generated.

[0067] Furthermore, regarding the slot 70 located on the left, it is arranged approximately symmetrically to the slot 70 located on the right on the sliding surface 7a, therefore detailed description is omitted.

[0068] Thus, even when the radial component of the relative movement of the slot 70 accompanying the eccentric rotation is difficult to act on the first wall surface 70a, for example, when the slot 70 arranged on the right is as described above, and the slot 70 arranged on the left is in a state where... Figure 3 (c) In the rotating state, the fluid in the groove 70 can also collide with the second wall surface 70c through the circumferential component, thereby generating high dynamic pressure. Therefore, high dynamic pressure can be generated over a relatively wide circumferential range between the sliding surfaces 7a and 8a.

[0069] Furthermore, the groove 70 has an opening on the inner diameter side, which allows fluid flowing into the groove 70 from the opening to be easily retained within the groove 70 due to centrifugal force. Therefore, the sliding surfaces 7a and 8a are less likely to be in a poor lubrication state, and a lubricating oil film is easily formed.

[0070] Furthermore, the tank 70 opens toward the back pressure chamber 50, which has a higher pressure than the low-pressure chamber 20. As a result, fluid can easily flow into the tank 70 from the opening due to the fluid pressure. Therefore, a higher dynamic pressure can be generated within the tank 70.

[0071] Furthermore, the side seal 7, on which the groove 70 is formed on the sliding surface 7a, has a narrower radial width compared to the thrust plate 8, which slides relatively. (Refer to...) Figure 1 and Figure 3 Therefore, between the sliding surfaces 7a and 8a that slide relative to each other during eccentric rotation, the entire sliding surface 7a of the side seal 7 is always located within the sliding area with the sliding surface 8a of the thrust plate 8 (see reference). Figure 3 It can reliably generate dynamic pressure through the 70 channel.

[0072] The embodiments of the present invention have been described above with reference to the accompanying drawings. However, the specific structure is not limited to these embodiments. Even if changes or additions are made without departing from the spirit of the present invention, they are also included in the present invention.

[0073] In the above embodiments, the application of the side seal 7 as a sliding component in the scroll compressor C used in the air conditioning system of automobiles, etc., has been described, but it is not limited to this. It can be applied to any rotating machine that includes an eccentric mechanism, such as a scroll expander compressor that integrates an expander and a compressor.

[0074] In addition, the fluid existing in the space inside and outside the sliding surface of the sliding component can be any of the following states: gas, liquid, or a mixture of gas and liquid.

[0075] Furthermore, in the above embodiment, the manner in which the groove 70 formed on the sliding surface 7a of the side seal 7 opens toward the inner diameter side has been described, but it is not limited to this; it could also be, for example... Figure 5 As shown in the side seal 107 of Modified Example 1, a plurality of slots 170 with outwardly oriented openings are arranged at equal intervals in the circumferential direction of the sliding surface 107a.

[0076] Alternatively, it could be, such as Figure 6 As shown in the modified example 2, the side seal 207 has grooves 270A opening to the inner diameter and grooves 270B opening to the outer diameter alternately formed in the circumferential direction of the sliding surface 207a.

[0077] Furthermore, in the above embodiment, the corners 70d and 70d of the first wall surface 70a and the second wall surfaces 70c, 70c are described as forming approximately right angles. However, this is not a limitation. It is possible for the first wall surface extending circumferentially along the inner periphery of the sliding surface in the groove and the second wall surface extending radially to be connected. For example, as shown in the example... Figure 7 As shown in (a) in variant example 3, the corners of the first and second walls are formed into acute angles.

[0078] Alternatively, it could be, such as Figure 7 As shown in variant example 4 (b), the corners are formed into obtuse angles.

[0079] Alternatively, it could be, such as Figure 7 As shown in Modification 5 (c), the corners are formed into an arc shape. Furthermore, the grooves in Modifications 3 to 5 can open to the space on the outer diameter side as in Modification 1, or they can open alternately to the space on the inner diameter side and the space on the outer diameter side as in Modification 2.

[0080] In addition, the groove 70 is not limited to a groove that is longer in the circumferential direction, but can also be a groove that is shorter in the circumferential direction, or a groove in which the first wall and the second wall have the same length.

[0081] Furthermore, in the above embodiment, the groove 70 formed on the sliding surface 7a of the side seal 7 was described as opening toward the back pressure chamber 50, which has a higher pressure than the low-pressure chamber 20. However, this is not a limitation; the groove may also open toward the low-pressure chamber 20. Additionally, the sliding member of the present invention only needs to have a sliding surface that slides relative to the sliding surface with eccentric rotation. It is not limited to environments where there is a pressure difference between the inside and outside of the sliding surface; it can also be used in environments where the pressures inside and outside the sliding surface are approximately the same. Furthermore, in the sliding member of the present invention, it is not necessary to function as a seal; it is sufficient to reduce friction on the sliding surface.

[0082] Furthermore, in the above embodiments, the side seal 7 with relatively sliding sliding surfaces 7a and 8a is described as being made of resin and the thrust plate 8 as being made of metal, but the material of the sliding component can be freely selected according to the usage environment, etc.

[0083] Furthermore, in the above embodiment, the method of forming a groove 70 on the sliding surface 7a of the side seal 7 has been described, but it is not limited to this. A groove may also be formed in the sliding region of the sliding surface 8a of the thrust plate 8, which is a sliding member having a sliding surface that slides relative to the sliding surface with eccentric rotation (see reference). Figure 3 Alternatively, grooves can be formed on both the sliding surface 7a of the side seal 7 and the sliding surface 8a of the thrust plate 8.

[0084] Furthermore, in the above embodiment, the structure in which the sliding surface 7a of the side seal 7, which is a sliding member, and the sliding surface 8a of the thrust plate 8 slide relative to each other during eccentric rotation has been described. However, this is not a limitation. It is also possible to have only one of the side seal and the thrust plate, and form a groove on the sliding surface that slides relative to each other during eccentric rotation. For example, in the case of having only the thrust plate, the groove may be formed on either or both of the sliding surface of the thrust plate, which is a sliding member, and the back surface of the end plate of the movable scroll. In addition, in the case of having only the side seal, the groove may be formed on the sliding surface of the side seal, which is a sliding member. In this case, the side seal also abuts against the inner circumferential surface of the inner shell and functions as a thrust bearing that bears the axial load of the movable scroll.

[0085] Alternatively, in the case where the side seal and thrust plate are not provided, and the back of the end plate of the movable scroll plate abuts against the inner circumferential surface of the inner shell to function as a thrust bearing bearing the axial load of the movable scroll plate, a groove may be formed on the sliding surface formed on the back of the end plate of the movable scroll plate.

[0086] Symbol Explanation

[0087] 1: Housing; 2: Rotating shaft; 2a: Eccentric part; 3: Inner shell; 4: Scroll compression mechanism; 6: Oil separator; 7: Side seal (sliding component); 7a: Sliding surface; 8: Thrust plate; 8a: Sliding surface; 10: Inlet; 13: Discharge passage; 14: Back pressure passage; 15: Inlet passage; 20: Low-pressure chamber; 30: High-pressure chamber; 40: Compression chamber; 41: Fixed scroll plate; 42: Movable scroll Disc; 50: Back pressure chamber; 70: Groove; 70a: First wall surface (arc surface); 70b: Bottom surface; 70c: Second wall surface (radial surface); 70d: Corner; 107: Side seal (sliding component); 107a: Sliding surface; 170: Groove; 207: Side seal (sliding component); 207a: Sliding surface; 270A: Groove; 270B: Groove; C: Scroll compressor; M: Drive motor; Q: Center.

Claims

1. An eccentric slide assembly, wherein, comprising: a first sliding member in a circular ring shape having a sliding surface, a second sliding member in a circular ring shape having a sliding surface, a rotating shaft, a movable scroll on which the first sliding member is mounted, and wherein the rotating shaft has an eccentric portion formed eccentrically with respect to an axis thereof, the movable scroll has a connecting portion fixed to the eccentric portion of the rotating shaft, wherein the sliding surface of the first sliding member is provided with grooves in which a plurality of space openings in which fluid exists are provided in at least either of an inner diameter side and an outer diameter side in a circumferential direction on the sliding surface, the entire sliding surface of the first sliding member is always positioned in a sliding region between the sliding surface of the first sliding member and the sliding surface of the second sliding member at any eccentric rotation angle of the sliding surface of the first sliding member with respect to the sliding surface of the second sliding member, the grooves are formed by connecting a first wall surface extending in a circumferential direction of the sliding surface and a second wall surface extending in a radial direction, and a circumferential dimension of the grooves is longer than a circumferential dimension of a land portion between adjacent grooves, so that a plurality of the grooves are densely formed in the circumferential direction of the sliding surface.

2. The eccentric sliding assembly according to claim 1, wherein an angle portion of the first wall surface and the second wall surface of the groove has a corner.

3. The eccentric sliding assembly according to claim 1, wherein the first wall surface is a circular arc surface having a center at a center of the sliding surface, and the second wall surface is a radial surface extending from the center of the sliding surface.

4. The eccentric sliding assembly according to claim 1, wherein the groove is a groove longer in the circumferential direction.

5. The eccentric sliding assembly according to claim 1, wherein the groove is a groove in which a space opening is provided in the inner diameter side.

6. The eccentric sliding assembly according to claim 1, wherein the groove is a groove in which a space opening is provided in the high pressure side.

7. The eccentric sliding assembly according to claim 1, wherein the sliding member is a sliding member narrower in a radial width among a pair of sliding members in relative sliding.

8. An eccentric slide assembly, wherein, comprising: a first sliding member in a circular ring shape having a sliding surface, a second sliding member in a circular ring shape having a sliding surface, a rotating shaft, a movable scroll on which the first sliding member is mounted, and wherein the rotating shaft has an eccentric portion formed eccentrically with respect to an axis thereof, the movable scroll has a connecting portion fixed to the eccentric portion of the rotating shaft, wherein the sliding surface of the first sliding member is provided with grooves in which a plurality of space openings in which fluid exists are provided in at least either of an inner diameter side and an outer diameter side in a circumferential direction on the sliding surface, the entire sliding surface of the first sliding member is always positioned in a sliding region between the sliding surface of the first sliding member and the sliding surface of the second sliding member at any eccentric rotation angle of the sliding surface of the first sliding member with respect to the sliding surface of the second sliding member, the grooves are formed by connecting a first wall surface extending in a circumferential direction of the sliding surface and a second wall surface extending in a radial direction, grooves in which a space opening is provided in the inner diameter side and grooves in which a space opening is provided in the outer diameter side are alternately formed in the circumferential direction of the sliding surface.

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