Compressor

Abstract

The purpose of the present invention is to suppress noise generated by contact between a recess and a ring. A compressor is provided with: a first housing (3) forming an outer shell; a fixed scroll; an orbiting scroll (6); a rotation prevention mechanism that prevents rotation of the orbiting scroll (6); and a lubricating oil supply unit for supplying lubricating oil to the rotation prevention mechanism. The rotation prevention mechanism has: a recess (32) formed on one of the orbiting scroll (6) side and the first housing (3) side; a ring (33) disposed in the recess (32) and having an outer peripheral surface (33b) facing an inner peripheral surface (32a) of the recess (32) with a gap therebetween; and a pin (34) provided on the other of the orbiting scroll (6) side and the first housing (3) side and engaged with an inner peripheral surface (33a) of the ring (33). The ratio of the axial length of the ring (33) to the gap formed between the bottom surface (32b) of the recess (32) and the axial end of the ring (33) is 0.01 or more and less than 0.06.

Description

Technical Field

[0001] This invention relates to a compressor. Background Technology

[0002] A scroll compressor is known, which comprises a pair of fixed scroll discs and a rotating scroll disc that mesh with each other to form a compression chamber. The rotating scroll disc compresses the refrigerant gas in the compression chamber by revolving relative to the fixed scroll discs.

[0003] The scroll compressor is equipped with a rotation-stopping mechanism to prevent the rotation of the rotating scroll disc. Examples of rotation-stopping mechanisms include a cross-coupling type or a pin-ring type. For example, Patent Document 1 discloses a scroll compressor equipped with a pin-ring type rotation-stopping mechanism.

[0004] Previous technical documents Patent documents Patent Document 1: Japanese Patent Application Publication No. 2022-112858 Summary of the Invention

[0005] The technical problem to be solved by the invention In a self-rotating stop mechanism having a ring housed in a recess and a pin engaging with the ring, noise generated by friction between the inner circumferential surface of the recess and the outer circumferential surface of the ring, or by friction between the bottom surface of the recess and the axial end of the ring, due to the load generated by the rotation of the rotary scroll, becomes a problem.

[0006] The present invention was made in view of this situation, and its object is to provide a compressor capable of suppressing noise generated by the contact between the recess and the ring.

[0007] means for solving technical problems To address the aforementioned issues, the compressor of the present invention employs the following means.

[0008] The compressor according to one aspect of the present invention comprises: a frame forming a housing; a fixed scroll plate housed in the frame and fixed to the frame side; a rotating scroll plate engaging with the fixed scroll plate and rotating relative to the fixed scroll plate; a rotation-stopping mechanism preventing the rotation of the rotating scroll plate; and a lubricating oil supply unit supplying lubricating oil to the rotation-stopping mechanism, the rotation-stopping mechanism having a recess formed on one side of the rotating scroll plate side or the frame side, a ring disposed in the recess and having its outer peripheral surface facing the inner peripheral surface of the recess with a gap, and a pin disposed on the other side of the rotating scroll plate side or the frame side and engaging with the inner peripheral surface of the ring, wherein the ratio of the axial length of the ring to the gap between the bottom surface of the recess and the axial end of the ring is 0.01 or more and less than 0.06.

[0009] Invention Effects According to the present invention, noise generated by the contact between the recess and the ring can be suppressed. Attached Figure Description

[0010] Figure 1 This is a longitudinal sectional view of the electric compressor according to an embodiment of the present invention.

[0011] Figure 2 This is a longitudinal sectional view of the pin ring structure according to an embodiment of the present invention.

[0012] Figure 3 This is a top view of the pin ring structure according to an embodiment of the present invention.

[0013] Figure 4 It is a graph showing the relationship between the ratio of the ring width to the axial clearance and the noise level. Detailed Implementation

[0014] Hereinafter, with reference to the accompanying drawings, one embodiment of the compressor according to the present invention will be described.

[0015] exist Figure 1 The image shows a longitudinal sectional view of the electric compressor 1 according to this embodiment.

[0016] The electric compressor 1 involved in this embodiment is an inverter-integrated electric compressor that integrates an inverter (not shown) with a drive motor 17.

[0017] The electric compressor 1 includes a housing 2 forming the outer shell, a scroll compression mechanism 7 housed in the housing 2, and a motor 17 that drives the scroll compression mechanism 7.

[0018] The housing 2 has a cylindrical first housing (frame) 3 extending along the central axis and one end side that closes the first housing 3 in the direction of the central axis. Figure 1 The second shell 4 (located on the lower end side).

[0019] A scroll compressor mechanism 7 is assembled on one end of the housing 2. The scroll compressor mechanism 7 has a pair of fixed scroll plates 5 and a rotating scroll plate 6. The scroll compressor mechanism 7 compresses the refrigerant gas. The high-pressure refrigerant gas compressed by the scroll compressor mechanism 7 is discharged into the discharge chamber 10 through the discharge port 8. The discharge port 8 is formed at the center of the fixed scroll plates 5. The refrigerant gas discharged into the discharge chamber 10 is discharged to the outside of the electric compressor 1 through the discharge port (not shown) provided on the housing 2.

[0020] The fixed scroll plate 5 is fixed to the second housing 4 by bolts or other fasteners (not shown). The rotating scroll plate 6 is rotatably supported on the thrust bearing 12 via a rotation-stopping mechanism 30. Details of the rotation-stopping mechanism 30 will be described later. The rotating scroll plate 6 rotates relative to the fixed scroll plate 5. Both the fixed scroll plate 5 and the rotating scroll plate 6 are made of aluminum, for example. However, the material of the fixed scroll plate 5 and the rotating scroll plate 6 is not limited to aluminum.

[0021] The fixed scroll 5 and the rotating scroll 6 are engaged in a meshing manner. A compression chamber 14 is formed between the fixed scroll 5 and the rotating scroll 6. The scroll compression mechanism 7 compresses the refrigerant in the compression chamber 14 by causing the rotating scroll 6 to rotate (revolve) so that the volume of the compression chamber 14 decreases from the outer peripheral side to the central side.

[0022] Motor 17 is assembled at the other end of cylindrical housing 2. Motor 17 has stator 15 and rotor 16. Drive shaft 18 is coupled to rotor 16. Drive shaft 18 is supported for free rotation by bearing 20 located near the center of housing 2 and bearing 21 located near the other end of housing 2. Crank pin 19 is provided at one end of drive shaft 18. The central axis of drive shaft 18 and the central axis of crank pin 19 are eccentric. Crank pin 19 is connected to rotary scroll 6. That is, drive shaft 18 connects motor 17 and scroll compressor mechanism 7. Motor 17 rotates rotary scroll 6 via drive shaft 18.

[0023] Furthermore, a driven crank mechanism (not shown) is provided between the crank pin 19 and the rotary scroll 6. The driven crank mechanism allows the rotation radius of the rotary scroll 6 to be variable. As an example of a driven crank mechanism, a driven crank mechanism of the oscillating linkage type can be given, for example.

[0024] A suction port (not shown) is provided at the other end of the housing 2 for drawing in low-pressure refrigerant gas from the refrigeration working cycle. The refrigerant gas drawn in through the suction port flows into the space 24 between the first housing 3 and one end of the motor 17. The low-pressure refrigerant gas flowing into the space 24 fills the housing 2. Specifically, the low-pressure refrigerant gas flowing into the space 24 flows towards the scroll compressor 7 and is drawn in and compressed by the scroll compressor 7. The refrigerant gas contains lubricating oil. The lubricating oil contained in the refrigerant gas is supplied together with the refrigerant gas to the scroll compressor 7 or the rotation-stopping mechanism 30 to lubricate each mechanism. That is, the suction port functions as a lubricating oil supply unit for supplying lubricating oil to the rotation-stopping mechanism 30.

[0025] On the other end side along the central axis of housing 2 (in) Figure 1An inverter housing 25 is provided on the upper side of the first housing 3. The other end of the first housing 3 is closed by the inverter housing 25. An inverter (not shown) that drives the motor 17 is housed inside the inverter housing 25. The inverter drives the motor 17 by converting DC power supplied from an external battery or the like into three-phase AC power of the required frequency and applying it to the motor 17 via terminals (not shown).

[0026] Next, the details of the rotation-stopping mechanism 30 will be explained.

[0027] The rotation-stopping mechanism 30 involved in this embodiment is a so-called pin-ring type rotation-stopping mechanism. The rotation-stopping mechanism 30 prevents the rotation of the rotary scroll disk 6. The rotation-stopping mechanism 30 has a plurality of (for example, 6 in this embodiment) pin-ring structures (rotation-stopping structures) 31. The 6 pin-ring structures 31 are arranged at equal intervals along the circumference with the central axis of the drive shaft 18 or the rotary scroll disk 6 as the center. That is, in this embodiment, since 6 pin-ring structures 31 are provided, the 6 pin-ring structures 31 are arranged at 60-degree intervals along the circumference.

[0028] Since the multiple pin ring structures 31 are all the same structure, the following description will focus on one pin ring structure 31 as an example.

[0029] like Figure 2 and Figure 3 As shown, the pin ring structure 31 has an annular hole (recess) 32 formed in the rotating scroll disk 6, a ring 33 accommodated in the annular hole 32, and a pin 34 engaged with the inner circumferential surface 33a of the ring 33.

[0030] The annular hole 32 is formed on the side of the end plate 6a of the rotating scroll disk 6 opposite to the side forming the compression chamber 14 (hereinafter referred to as "back side 6b") (reference). Figure 1 The annular hole 32 is recessed to a specified depth from the back surface 6b of the rotating scroll disk 6. (As shown) Figure 2 As shown, the annular hole 32 is a bottomed concave portion. When viewed from above, the annular hole 32 appears to be a perfect circle. That is, the inner circumferential surface 32a of the annular hole 32 is a cylindrical surface.

[0031] like Figure 2 and Figure 3 As shown, ring 33 is a cylindrical component with a specified thickness. Ring 33 is disposed within annular hole 32. Figure 2 As shown, the length of the ring 33 along its central axis (hereinafter referred to as the "axial direction") is shorter than the depth of the annular hole 32. One axial end of the ring 33 abuts against the first housing 3. A gap (hereinafter referred to as the "axial gap") is formed between the ring 33 and the bottom surface 32b of the annular hole 32. That is, the ring 33 is suspended within the annular hole 32. The length of the axial gap is G2.

[0032] The ring 33 is configured such that its outer peripheral surface 33b faces the inner peripheral surface 32a of the annular hole 32. The ring 33 is formed, for example, from high-carbon chromium bearing steel (SUJ2). However, the material of the ring 33 is not limited to high-carbon chromium bearing steel (SUJ2). In this embodiment, the outer diameter of the ring 33 is set to be 13 mm or more and 15.5 mm or less. However, the value of the outer diameter of the ring 33 is just an example and is not limited to this value.

[0033] A gap (hereinafter referred to as the "radial gap") is formed between the inner circumferential surface 32a of the annular hole 32 and the outer circumferential surface 33b of the ring 33. The length of the radial gap is G1. When a portion of the outer circumferential surface 33b of the ring 33 is in contact with the inner circumferential surface 32a of the annular hole 32, the length of the longest portion of the radial gap (hereinafter simply referred to as the "length of the radial gap") is 0.1 mm or more and 0.6 mm or less. That is, the outer diameter of the ring 33 is smaller than the diameter of the annular hole 32. In detail, the outer diameter of the ring 33 is smaller than the diameter of the annular hole 32 than the length of the radial gap.

[0034] like Figure 2 As shown, a pin 34, configured to correspond to the ring 33 disposed in the annular hole 32, is fixed to the first housing 3. Figure 2 and Figure 3 As shown, pin 34 engages with the inner circumferential surface 33a of ring 33. The front end of pin 34 is separated from the bottom surface 32b of ring hole 32.

[0035] A gap (axial gap and radial gap) is formed between ring 33 and annular hole 32. By retaining lubricating oil in this gap, noise is reduced by the damping force generated by the lubricating oil. The length G2 of the axial gap is shorter than the length G1 of the radial gap.

[0036] The ratio of the lengths of the axial clearance and the radial clearance is set to a predetermined ratio. Specifically, the length of each clearance is set such that the ratio of the length G1 of the radial clearance to the length G2 of the axial clearance is 0.25 or more and less than 1.0. Preferably, the length of each clearance is set such that the ratio of the length G1 of the radial clearance to the length G2 of the axial clearance is 0.25 or more and less than 0.5.

[0037] Furthermore, the axial clearance is determined such that the axial length L of the ring 33 (hereinafter referred to as the "width of the ring 33") is in a predetermined ratio to the length G2 of the axial clearance. Specifically, the ratio of the width of the ring 33 to the length G2 of the axial clearance (hereinafter sometimes referred to as the "clearance ratio") is 0.01 or more and less than 0.06. Preferably, the clearance ratio is 0.02 or more and less than 0.04.

[0038] Next, the operation of the rotation-stopping mechanism 30 will be explained.

[0039] The rotation-stopping mechanism 30 moves relative to the pin 34 and the ring 33 as the rotary scroll 6 rotates, thereby bringing the pin 34 into contact with the ring 33 and preventing the rotary scroll 6 from rotating. In this embodiment, the pin 34, fixed to the housing 2, does not move, while the ring 33 provided on the rotary scroll 6 moves.

[0040] Multiple pin ring structures 31 are configured to bear the load sequentially as the rotary scroll disk 6 rotates. That is, the rotation-stopping mechanism 30 stops the rotation of the rotary scroll disk 6 by sequentially transferring the rotation-stopping function among the multiple pin ring structures 31 as the rotary scroll disk 6 rotates (in other words, switching the pin ring structure 31 that bears the rotation-stopping mechanism 30).

[0041] According to this embodiment, the following effects are achieved.

[0042] In this embodiment, a gap (radial gap) is formed between the inner circumferential surface 32a of the annular hole 32 and the outer circumferential surface 33b of the ring 33. As a result, lubricating oil flows into and remains within the radial gap. The lubricating oil retained in the radial gap mitigates the impact when the annular hole 32 contacts the ring 33. Therefore, noise generated by the contact between the annular hole 32 and the ring 33 can be suppressed.

[0043] If the gap (axial clearance) between the bottom surface 32b of the annular hole 32 and the axial end of the ring 33 is large, the lubricating oil flowing into the radial clearance can easily flow out through the axial clearance, which may not be sufficient to suppress the noise generated by the contact between the annular hole 32 and the ring 33. In this embodiment, the ratio (clearance ratio) of the axial length of the ring 33 to the axial clearance is less than 0.06. More preferably, the clearance ratio is less than 0.04. Thus, because the axial clearance is small, it is difficult for lubricating oil to flow out from the radial clearance, thereby suppressing the noise generated by the contact between the annular hole 32 and the ring 33.

[0044] On the other hand, if the axial clearance is too small, a lubricating oil film cannot be formed in the axial clearance, causing the ring 33 to contact the bottom surface 32b of the annular hole 32. This makes the ring 33's behavior unstable and may lead to increased noise. In this embodiment, the ratio of the ring 33's width to the axial clearance is 0.01 or more, preferably 0.02 or more. This ensures that the axial clearance is not too small, allowing a suitable lubricating oil film to form in the axial clearance. Therefore, contact between the ring 33 and the bottom surface 32b of the annular hole 32 can be suppressed, thus stabilizing the ring 33's behavior. Consequently, noise can be suppressed.

[0045] Regarding the noise reduction effect, using Figure 4 Please provide an explanation. Figure 4 In the diagram, the vertical axis represents the noise level (dB(A)) and the horizontal axis represents the clearance ratio.

[0046] like Figure 4 As shown, the noise level increases near a clearance ratio of 0. Furthermore, the noise level gradually decreases within a clearance ratio range from 0 to less than 0.01. The noise level is lowest at a clearance ratio of 0.01, and gradually increases up to a clearance ratio of 0.08. Figure 4 As shown, the noise level is sufficiently low within a gap ratio range of 0.01 or higher and less than 0.06.

[0047] Furthermore, in this embodiment, the ratio of radial clearance to axial clearance is less than 1.0, preferably 0.5 or less. Thus, by making the axial clearance smaller than the radial clearance, the axial clearance can be sufficiently reduced, making it difficult for lubricating oil to flow out from the radial clearance. Therefore, noise generated by the contact between the annular hole 32 and the ring 33 can be suppressed.

[0048] Furthermore, in this embodiment, the ratio of radial clearance to axial clearance is 0.25 or higher. This prevents the axial clearance from becoming too small, allowing a suitable film of lubricating oil to form within the axial clearance. Consequently, contact between the ring 33 and the bottom surface 32b of the annular hole 32 can be suppressed, thus stabilizing the behavior of the ring 33. Therefore, noise can be suppressed more effectively.

[0049] Furthermore, the present invention is not limited to the inventions involved in the above embodiments, and can be appropriately modified within the scope of its spirit.

[0050] For example, in the embodiments described above, the electric compressor 1 is an example of an inverter-integrated electric compressor, but the present invention is not limited thereto. For example, the electric compressor 1 may also be an electric compressor without an inverter. Furthermore, the electric compressor 1 may also be an electric compressor with an inverter separately provided.

[0051] The compressor described in the above-described embodiments can be understood as follows.

[0052] The compressor according to the first aspect of the present invention comprises: a frame 3 forming a housing; a fixed scroll 5 housed in the frame and fixed to the frame side; a rotating scroll 6 engaging with the fixed scroll and rotating relative to the fixed scroll; a rotation-stopping mechanism 30 preventing the rotation of the rotating scroll; and a lubricating oil supply unit supplying lubricating oil to the rotation-stopping mechanism. The rotation-stopping mechanism has a recess 32 formed on one side of the rotating scroll side or the frame side, a ring 33 disposed in the recess and with its outer peripheral surface 33b facing the inner peripheral surface 32a of the recess with a gap, and a pin 34 disposed on the other side of the rotating scroll side or the frame side and engaging with the inner peripheral surface 33a of the ring. The ratio of the axial length of the ring to the gap between the bottom surface 32b of the recess and the axial end of the ring is 0.01 or more and less than 0.06.

[0053] In the above structure, a gap is formed between the inner circumferential surface of the recess and the outer circumferential surface of the ring. Lubricating oil flows into the gap between the inner circumferential surface of the recess and the outer circumferential surface of the ring (hereinafter referred to as the "radial gap"). The lubricating oil flowing into the radial gap mitigates the impact when the recess contacts the ring. Therefore, noise generated by the contact between the recess and the ring can be suppressed.

[0054] If the gap between the bottom surface of the recess and the axial end of the ring (hereinafter referred to as the "axial clearance") is large, the lubricating oil flowing into the radial clearance can easily flow out through the axial clearance, which may not be able to adequately suppress the noise generated by the contact between the recess and the ring. In the above structure, the ratio of the axial length of the ring (hereinafter referred to as the "ring width") to the axial clearance is less than 0.06. Thus, because the axial clearance is small, it is difficult for lubricating oil to flow out from the radial clearance, thereby suppressing the noise generated by the contact between the recess and the ring.

[0055] On the other hand, if the axial clearance is too small, a lubricating oil film cannot be formed within the axial clearance. Therefore, the ring contacts the bottom surface of the recess (rotating scroll or frame), and the ring's behavior becomes unstable, potentially leading to increased noise. In the above structure, the ratio of the ring width to the axial clearance is 0.01 or more. Thus, since the axial clearance is not too small, a lubricating oil film can be appropriately formed within the axial clearance. Therefore, contact between the ring and the bottom surface of the recess can be suppressed, thereby stabilizing the ring's behavior. Therefore, noise can be suppressed.

[0056] In the compressor according to the second aspect of the present invention, in the first aspect described above, the ratio of the axial length of the ring to the gap between the bottom surface of the recess and the axial end of the ring is 0.02 or more and less than 0.04.

[0057] In the above structure, the ratio of the ring width to the axial clearance is less than 0.04. Thus, because the axial clearance is sufficiently small, lubricating oil is less likely to flow out from the radial clearance, thereby more effectively suppressing noise generated by the contact between the recess and the ring.

[0058] Furthermore, the ratio of the ring width to the axial clearance is 0.02 or higher. This ensures that the axial clearance is not too small, allowing for the appropriate formation of a lubricating oil film within the axial clearance. Consequently, contact between the ring and the bottom surface of the recess can be suppressed, thus stabilizing the ring's behavior. Consequently, noise can be suppressed more effectively.

[0059] In the compressor according to the third aspect of the present invention, in the first or second aspect described above, the ratio of the gap between the inner peripheral surface of the recess and the outer peripheral surface of the ring to the gap between the bottom surface of the recess and the axial end of the ring is 0.25 or more and less than 1.0.

[0060] In the above structure, the ratio of radial clearance to axial clearance is less than 1.0. Thus, by making the axial clearance smaller than the radial clearance, the axial clearance can be sufficiently reduced, making it difficult for lubricating oil to flow out from the radial clearance. Therefore, noise generated by the contact between the recess and the ring can be suppressed.

[0061] Furthermore, in the above structure, the ratio of radial clearance to axial clearance is 0.25 or higher. This prevents the axial clearance from becoming too small, allowing for the appropriate formation of a lubricating oil film within the axial clearance. Consequently, contact between the ring and the bottom surface of the recess can be suppressed, thus stabilizing the ring's behavior. Consequently, noise can be suppressed more effectively.

[0062] In the compressor according to the fourth aspect of the present invention, in the third aspect described above, the ratio of the gap between the inner peripheral surface of the recess and the outer peripheral surface of the ring to the gap between the bottom surface of the recess and the axial end of the ring is 0.25 or more and 0.5 or less.

[0063] In the above structure, the ratio of radial clearance to axial clearance is 0.5 or less. Thus, because the axial clearance is sufficiently small, lubricating oil is less likely to flow out from the radial clearance, thereby more effectively suppressing noise generated by the contact between the recess and the ring.

[0064] Furthermore, the ratio of radial clearance to axial clearance is 0.25 or higher. This prevents the axial clearance from becoming too small, allowing for the appropriate formation of a lubricating oil film within the axial clearance. Consequently, contact between the ring and the bottom surface of the recess can be suppressed, thus stabilizing the ring's behavior. Consequently, noise can be suppressed more effectively.

[0065] Symbol Explanation 1-Electric compressor, 2-Housing, 3-First housing, 4-Second housing, 5-Fixed scroll plate, 6-Rotating scroll plate, 6a-End plate, 6b-Back side, 7-Scroll compression mechanism, 8-Discharge port, 10-Discharge chamber, 12-Thrust bearing, 14-Compression chamber, 15-Stator, 16-Rotor, 17-Motor, 18-Drive shaft, 19-Crank pin, 20-Bearing, 21-Bearing, 24-Space section, 25-Inverter housing section, 30-Rotation prevention mechanism, 31-Pin ring structure, 32-Ring hole, 32a-Inner circumferential surface, 32b-Bottom surface, 33-Ring, 33a-Inner circumferential surface, 33b-Outer circumferential surface, 34-Pin.

Claims

1. A compressor comprising: a frame forming a housing; A fixed scroll plate is housed within the frame and fixed to the side of the frame; A rotating scroll plate engages with the fixed scroll plate and rotates relative to the fixed scroll plate; The rotation-stopping mechanism prevents the rotation of the rotary scroll disk; and The lubricating oil supply unit supplies lubricating oil to the rotation-stopping mechanism. The rotation-stopping mechanism has a recess formed on one side of the rotating scroll disk or the frame side, a ring disposed in the recess with its outer peripheral surface facing the inner peripheral surface of the recess through a gap, and a pin disposed on the other side of the rotating scroll disk or the frame side and engaging with the inner peripheral surface of the ring. The ratio of the axial length of the ring to the gap between the bottom surface of the recess and the axial end of the ring is greater than 0.01 and less than 0.

06.

2. The compressor according to claim 1, wherein, The ratio of the axial length of the ring to the gap between the bottom surface of the recess and the axial end of the ring is greater than 0.02 and less than 0.

04.

3. The compressor according to claim 1 or 2, wherein, The ratio of the gap between the inner circumferential surface of the recess and the outer circumferential surface of the ring to the gap between the bottom surface of the recess and the axial end of the ring is 0.25 or more and less than 1.

0.

4. The compressor according to claim 3, wherein, The ratio of the gap between the inner circumferential surface of the recess and the outer circumferential surface of the ring to the gap between the bottom surface of the recess and the axial end of the ring is 0.25 or more and 0.5 or less.

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