Compressor

Abstract

To suppress noise caused by contact between a recession and a ring.SOLUTION: An electric compressor includes a housing which forms an outer shell, a fixed scroll which is stored in the housing and is fixed to the housing side, a turning scroll which is meshed with the fixed scroll and turns with respect to the fixed scroll, a rotation inhibiting mechanism 30 for inhibiting rotation of the turning scroll, and a lubricating oil supply part for supplying lubricating oil to the rotation inhibiting mechanism 30. The rotation inhibiting mechanism 30 includes a ring hole 32 formed on the turning scroll, a ring 33 arranged in the ring hole 32 and having an outer peripheral surface 33b facing an inner peripheral surface 32a of the ring hole 32, and a pin 34 provided in the housing and fitted with an inner peripheral surface 33a of the ring 33. A gap G formed between the inner peripheral surface 32a of the ring hole 32 and the outer peripheral surface 33b of the ring 33 is 0.1 mm or more and 0.6 mm or less.SELECTED DRAWING: Figure 2

Description

[Technical Field]

[0001] The present disclosure relates to a compressor. [Background technology]

[0002] A scroll compressor is known that includes a pair of fixed and orbiting scrolls that are meshed with each other to form a compression chamber. The orbiting scroll revolves around the fixed scroll to compress refrigerant gas in the compression chamber.

[0003] A scroll compressor is provided with a rotation-preventing mechanism to prevent the orbiting scroll from rotating. Examples of the rotation-preventing mechanism include an Oldham link type rotation-preventing mechanism and a pin-and-ring type rotation-preventing mechanism. For example, Patent Document 1 discloses a scroll compressor equipped with a pin-and-ring type rotation-preventing mechanism.

[0004] Patent Document 1 describes a scroll compressor in which a pin-and-ring coupling is disposed between a movable scroll and an end face of a front housing. This pin-and-ring coupling has a movable pin fixed to the movable scroll, a fixed pin fixed to the front housing, and a ring into which the movable pin and the fixed pin are inserted. The ring is housed in a recess formed in the housing and moves in sliding contact with the bottom surface of the recess in conjunction with the revolution of the movable scroll. [Prior art documents] [Patent documents]

[0005] [Patent Document 1] Japanese Patent Application Laid-Open No. 2001-132670 Summary of the Invention [Problem to be solved by the invention]

[0006] In conventional rotation-preventing mechanisms that have a ring housed in a recess and a pin that engages with the ring, the gap formed between the inner peripheral surface of the recess and the outer peripheral surface of the ring has been reduced. This is because reducing the gap reduces Hertzian stress and prevents damage to the recess. However, as long as there is a gap between the inner peripheral surface of the recess and the outer peripheral surface of the ring, the load generated by the orbiting scroll orbiting causes the inner peripheral surface of the recess to collide with the outer peripheral surface of the ring. This has caused a problem of noise when the ring collides with the recess.

[0007] The present disclosure has been made in view of the above circumstances, and has an object to provide a compressor that can suppress noise caused by contact between the recess and the ring. [Means for solving the problem]

[0008] In order to solve the above problems, the compressor of the present disclosure employs the following measures. The compressor according to one aspect of the present disclosure has an outer shell. The housing has a suction port, and the suction port receives low-pressure refrigerant gas from the refrigeration cycle. a housing; a fixed scroll accommodated in the housing and fixed to the housing side; an orbiting scroll that meshes with the fixed scroll and orbits relative to the fixed scroll; a rotation-preventing mechanism that prevents the orbiting scroll from rotating on its own axis; and a lubricating oil supply unit that supplies lubricating oil to the rotation-preventing mechanism, wherein the rotation-preventing mechanism has a recess formed on one of the orbiting scroll side and the housing side, a ring that is disposed within the recess and whose outer peripheral surface faces the inner peripheral surface of the recess, and a pin that is provided on the other of the orbiting scroll side and the housing side and engages with the inner peripheral surface of the ring, and a gap is formed between the inner peripheral surface of the recess and the outer peripheral surface of the ring, and the longest part of the gap has a length of 0.1 mm or more and 0.6 mm or less when a portion of the outer peripheral surface of the ring is in contact with the inner peripheral surface of the recess. This has the function of suppressing noise caused by contact between the recess and the ring. , The aforementioned From the refrigeration cycle The aforementioned Compresses low-pressure refrigerant gas. [Effects of the Invention]

[0009] According to the present disclosure, noise caused by contact between the recess and the ring can be suppressed. [Brief explanation of the drawings]

[0010] [Figure 1] FIG. 1 is a longitudinal sectional view of an electric compressor according to an embodiment of the present disclosure. [Figure 2] FIG. 1 is a plan view of a pin ring structure according to an embodiment of the present disclosure. [Figure 3] FIG. 10 is a schematic diagram illustrating a region where a load acts on each ring hole according to an embodiment of the present disclosure. [Figure 4] 10 is a graph showing the relationship between the size of the gap between the ring and the ring hole and the noise level. [Figure 5] FIG. 10 is a schematic plan view showing a ring hole according to a second embodiment of the present disclosure. [Figure 6] FIG. 6 is a diagram showing a modification of FIG. 5. DETAILED DESCRIPTION OF THE INVENTION

[0011] Hereinafter, an embodiment of a compressor according to the present disclosure will be described with reference to the drawings.

[0012] [First embodiment] Hereinafter, a first embodiment of the present disclosure will be described with reference to FIGS. FIG. 1 shows a vertical cross-sectional view of an electric compressor 1 according to this embodiment. The electric compressor 1 according to this embodiment is an inverter-integrated electric compressor in which an inverter (not shown) that drives the motor 17 is integrally incorporated.

[0013] The electric compressor 1 includes a housing (casing) 2 that forms an outer shell, a scroll compression mechanism 7 housed in the housing 2, and a motor 17 that drives the scroll compression mechanism 7.

[0014] The housing 2 has a cylindrical first housing 3 extending along the central axis, and a second housing 4 closing one end side (lower end side in FIG. 1) of the first housing 3 in the central axis direction.

[0015] The scroll compression mechanism 7 is incorporated into one end of the housing 2. The scroll compression mechanism 7 has a pair of fixed scrolls 5 and an orbiting scroll 6. The scroll compression mechanism 7 compresses refrigerant gas. The high-pressure refrigerant gas compressed by the scroll compression mechanism 7 is discharged into a discharge chamber 10 through a discharge port 8. The discharge port 8 is formed in the center of the fixed scroll 5. The refrigerant gas discharged into the discharge chamber 10 is discharged to the outside of the electric compressor 1 through a discharge port (not shown) provided in the housing 2.

[0016] The fixed scroll 5 is fixed to the second housing 4 by fasteners such as bolts (not shown). The orbiting scroll 6 is rotatably supported by the thrust bearing 12 via a rotation-preventing mechanism 30. Details of the rotation-preventing mechanism 30 will be described later. The orbiting scroll 6 orbits relative to the fixed scroll 5. The fixed scroll 5 and the orbiting scroll 6 are made of, for example, aluminum. Note that the material of the fixed scroll 5 and the orbiting scroll 6 is not limited to aluminum.

[0017] The fixed scroll 5 and the orbiting scroll 6 are engaged to be meshed with each other. A compression chamber 14 is formed between the fixed scroll 5 and the orbiting scroll 6. The scroll compression mechanism 7 compresses the refrigerant in the compression chamber 14 by the orbiting scroll 6 orbiting (revolving) so that the volume of the compression chamber 14 decreases from the outer periphery toward the center.

[0018] The motor 17 is incorporated into the other end of the cylindrical housing 2. The motor 17 has a stator 15 and a rotor 16. A drive shaft 18 is coupled to the rotor 16. The drive shaft 18 is rotatably supported by a bearing 20 installed near the center of the housing 2 and a bearing 21 installed near the other end of the housing 2. A crank pin 19 is provided at one end of the drive shaft 18. The drive shaft 18 and the crank pin 19 have eccentric central axes. The crank pin 19 is connected to the orbiting scroll 6. In other words, the drive shaft 18 connects the motor 17 and the scroll compression mechanism 7. The motor 17 orbits the orbiting scroll 6 via the drive shaft 18. In addition, a driven crank mechanism (not shown) is provided between the crank pin 19 and the orbiting scroll 6. The driven crank mechanism changes the orbiting radius of the orbiting scroll 6. An example of the driven crank mechanism is a swing link type driven crank mechanism.

[0019] The other end of the housing 2 is provided with a suction port (not shown) for drawing in low-pressure refrigerant gas from the refrigeration cycle. The refrigerant gas drawn in from the suction port flows into a space 24 between the first housing 3 and one end of the motor 17. The low-pressure refrigerant gas that flows into the space 24 fills the housing 2. Specifically, the low-pressure refrigerant gas that flows into the space 24 flows to the scroll compression mechanism 7, where it is sucked into and compressed by the scroll compression mechanism 7. The refrigerant gas contains lubricating oil. The lubricating oil contained in the refrigerant gas is supplied to the scroll compression mechanism 7 and the rotation-preventing mechanism 30 together with the refrigerant gas, lubricating these mechanisms. In other words, the suction port functions as a lubricating oil supply unit that supplies lubricating oil to the rotation-preventing mechanism 30.

[0020] An inverter accommodating section 25 is provided at the other end (top end in FIG. 1 ) of the housing 2 in the direction along the central axis. The other end of the first housing 3 is closed by the inverter accommodating section 25. An inverter (not shown) that drives the motor 17 is accommodated inside the inverter accommodating section 25. The inverter converts DC power supplied from an external battery or the like into three-phase AC power of a required frequency and applies it to the motor 17 via terminals (not shown), thereby driving the motor 17.

[0021] Next, the rotation-preventing mechanism 30 will be described in detail. The rotation-preventing mechanism 30 according to this embodiment is a so-called pin-ring type rotation-preventing mechanism. The rotation-preventing mechanism 30 prevents the orbiting scroll 6 from rotating on its axis. The rotation-preventing mechanism 30 has a plurality of (six, for example, in this embodiment) pin-ring structures (rotation-preventing structures) 31 (see FIG. 3). The plurality of pin-ring structures 31 are arranged at equal intervals in the circumferential direction around the central axis of the drive shaft 18 or the orbiting scroll 6. That is, in this embodiment, six pin-ring structures 31 are provided, and the six pin-ring structures 31 are arranged at 60-degree intervals in the circumferential direction.

[0022] Since the multiple pin-ring structures 31 each have the same structure, in principle, one pin-ring structure 31 will be described below as a representative. As shown in Figures 1 and 2, the pin-ring structure 31 includes a ring hole (recess) 32 formed in the orbiting scroll 6, a ring 33 accommodated in the ring hole 32, and a pin 34 that engages with the inner surface 33a of the ring 33.

[0023] As shown in FIG. 3, the multiple ring holes 32 are arranged side by side at a predetermined interval on the end plate 6a of the orbiting scroll 6. Specifically, the multiple ring holes 32 are arranged side by side in the circumferential direction around the center point of the orbiting scroll 6. The ring holes 32 are formed on the surface (hereinafter referred to as the "back surface 6b") opposite the surface of the end plate 6a of the orbiting scroll 6 that forms the compression chamber 14. The ring hole 32 is recessed to a predetermined depth from the back surface 6b of the orbiting scroll 6. The ring hole 32 is a recess with a bottom. The ring hole 32 has a perfect circular shape in a plan view. In other words, the inner peripheral surface 32a of the ring hole 32 is a cylindrical surface.

[0024] The ring 33 is a cylindrical member having a predetermined thickness. The length of the ring 33 in the central axial direction is approximately the same as the depth of the ring hole 32. The ring 33 is disposed within the ring hole 32. The ring 33 is disposed so that its outer peripheral surface 33b faces the inner peripheral surface 32a of the ring hole 32. The ring 33 is formed of, for example, high carbon chromium bearing steel (SUJ2). Note that 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 13 mm or more and 15.5 mm or less. Note that the value of the outer diameter of the ring 33 is an example and is not limited to this value.

[0025] A gap G is formed between the inner peripheral surface 32a of the ring hole 32 and the outer peripheral surface 33b of the ring 33. The length of the gap G at its longest point when part of the outer peripheral surface 33b of the ring 33 is in contact with the inner peripheral surface 32a of the ring hole 32 (hereinafter simply referred to as the "length of the gap G") is 0.1 mm or more and 0.6 mm or less. In other words, the outer diameter of the ring 33 is smaller than the diameter of the ring hole 32. In particular, the outer diameter of the ring 33 is smaller than the diameter of the ring hole 32 by the length of the gap G.

[0026] The multiple pins 34 are arranged to correspond to the rings 33 arranged in each ring hole 32. Specifically, the multiple pins 34 are arranged side by side at equal intervals in the circumferential direction around the central axis of the drive shaft 18. As shown in FIG. 1, the pins 34 are fixed to the first housing 3. As shown in FIG. 2, the pins 34 engage with the inner peripheral surface 33a of the ring 33. The tips of the pins 34 are spaced apart from the bottom surface of the ring hole 32.

[0027] The multiple pin ring structures 31 are arranged so as to receive a load in turn in accordance with the orbiting motion of the orbiting scroll 6. In other words, the rotation-preventing mechanism 30 prevents the rotation of the orbiting scroll 6 by passing the rotation-preventing function between the multiple pin ring structures 31 in turn in accordance with the orbiting motion of the orbiting scroll 6 (in other words, by switching the pin ring structure 31 that is responsible for the rotation-preventing mechanism 30).

[0028] Furthermore, the inner circumferential surface 32a of the ring hole 32 of each pin-ring structure 31 has a load area A1 over a predetermined angular range that receives a load from the pin 34 as the orbiting scroll 6 orbits. Specifically, the load area A1 of the ring hole 32 receives the load from the pin 34 via the ring 33. As shown in FIG. 3 , the load areas A1 of each ring hole 32 are disposed so as to be offset by 60 degrees when the back surface 6b of the end plate 6a of the orbiting scroll 6 is viewed in plan. The load area A1 of each ring hole 32 is disposed so as to form an arc of angle θ (60 degrees in this embodiment) when the back surface 6b of the end plate 6a of the orbiting scroll 6 is viewed in plan.

[0029] Next, the behavior of the rotation-preventing mechanism 30 will be described. In the rotation-preventing mechanism 30, the pin 34 and the ring 33 move relative to each other as the orbiting scroll 6 orbits, causing the pin 34 and the ring 33 to come into contact with each other, and this contact prevents the rotation of the orbiting scroll 6. In this embodiment, the pin 34 fixed to the housing 2 does not move, but the ring 33 provided on the orbiting scroll 6 moves. Next, the behavior of each pin-ring structure 31 will be described. When the orbiting scroll 6 orbits, one of the six pin-ring structures 31 first performs its rotation-preventing function. Specifically, as the ring 33 moves relative to the pin 34, the inner circumferential surface 33a of the ring 33 provided in one pin-ring structure 31 receives a load from the pin 34. As the movement of the ring hole 32 and the ring 33 is restricted by the pin 34 in this manner, the rotation of the orbiting scroll 6 is prevented. The ring 33 moves along the outer circumferential surface of the pin 34 through a predetermined angular range (60 degrees in this embodiment) while receiving the load. As a result, the load area A1 of the ring hole 32 also receives the load via the ring 33. When the ring 33 and the ring hole 32 move through the predetermined angular range, the rotation-preventing mechanism 30 switches the pin-ring structure 31 that performs the rotation-preventing function. Specifically, the pin-ring structure 31 is switched to the pin-ring structure 31 located forward in the orbiting direction of the orbiting scroll 6. This pin ring structure 31 similarly prevents the rotation of the orbiting scroll 6. In this way, the rotation-preventing mechanism 30 prevents the rotation of the orbiting scroll 6 by repeatedly transferring the rotation-preventing function between the multiple pin ring structures 31.

[0030] According to this embodiment, the following advantageous effects are achieved. In this embodiment, the length of the gap G formed between the ring hole 32 and the ring 33 is set to be equal to or greater than 0.1 mm and equal to or less than 0.6 mm. This allows the lubricating oil supplied to the rotation-preventing mechanism 30 to easily flow into the gap G. The lubricating oil that flows into the gap G reduces the impact when the ring hole 32 and the ring 33 come into contact. Therefore, noise caused by contact between the ring hole 32 and the ring 33 can be suppressed. The noise caused by contact between the ring hole 32 and the ring 33 is, for example, noise that occurs when the pin 34 and the ring 33, which have the function of preventing rotation, switch positions.

[0031] Next, the noise reduction effect of the rotation-preventing mechanism 30 according to this embodiment will be described using the graph in Fig. 4. Fig. 4 shows the results of an experiment investigating the relationship between the length of the gap G and the noise level. In Fig. 4, the horizontal axis represents the length of the gap G, and the vertical axis represents the noise level. As shown in Figure 4, when the length of the gap G is less than 0.1 mm, the noise level is relatively high. This is thought to be because it is difficult for the lubricating oil to flow into the gap G when the length of the gap G is less than 0.1 mm. When the length of the gap G is 0.1 mm, the noise level drops sharply compared to when the length is less than 0.1 mm. This is because the lubricating oil flows into the gap G favorably when the length of the gap G is 0.1 mm. It can be seen that when the length of gap G is in the range of 0.1 mm or more and less than 0.5 mm, the noise level decreases as the length of gap G increases. When the length of gap G is 0.5 mm or more, the noise level gradually increases. However, it can be seen that when the length of gap G is 0.6 mm or less, the noise level is sufficiently low. As can be seen from FIG. 4, noise can be suppressed when the length of the gap G is 0.1 mm or more and 0.6 mm or less. The graph of FIG. 4 is suitable for the case where the outer diameter of the ring 33 is 13 mm or more and 15.5 mm or less.

[0032] Second Embodiment Next, a second embodiment of the present disclosure will be described with reference to FIG. This embodiment differs from the first embodiment in that a storage portion is formed in the ring hole 32. Since this embodiment is similar to the first embodiment except for the formation of a storage portion, the same components are denoted by the same reference numerals and detailed description thereof will be omitted.

[0033] As shown in FIG. 5, a reservoir 41 recessed radially outward is formed on the inner circumferential surface 42a of the ring hole 42 according to this embodiment. The reservoir 41 is formed in a rectangular shape in a plan view. The reservoir 41 is formed in an area other than the load area A1 (hereinafter referred to as the "anti-load area A2"). In this embodiment, the reservoir 41 is disposed so as to include a circumferential midpoint C of the anti-load area A2. In other words, the reservoir 41 is provided at a position farthest from the load area A1. The reservoirs 41 may be formed in all of the ring holes 32 or in only some of the ring holes 32 .

[0034] According to this embodiment, the following advantageous effects are achieved. In this embodiment, the lubricating oil supplied to the rotation-preventing mechanism 30 is stored in the storage portion 41. Because the storage portion 41 is formed on the inner circumferential surface 42a of the ring hole 42, when the amount of lubricating oil held in the gap G between the inner circumferential surface 42a of the ring hole 42 and the outer circumferential surface 33b of the ring 33 becomes low, the lubricating oil stored in the storage portion 41 is guided to the gap G. Therefore, the lubricating oil is more suitably held in the gap G. This makes it possible to further suppress noise caused by contact between the ring hole 42 and the ring 33.

[0035] Furthermore, if a storage portion is formed in the load region A1, the load from the pin 34 due to the orbiting motion of the orbiting scroll 6 may cause the ring 33 to be deformed so as to be pushed into the storage portion 41. Furthermore, the storage portion 41 itself may be damaged by the load from the pin 34. On the other hand, in this embodiment, the storage portion 41 is formed in the anti-load region A2. This makes it possible to suppress deformation and damage to the ring 33. Furthermore, it is possible to suppress damage to the storage portion 41 due to the load from the pin 34.

[0036] [Modification] As shown in Figure 6, the entire storage section 51 may be provided on the inner surface 52a of the ring hole 52 forward of the circumferential midpoint C of the anti-load region A2 in the orbiting direction of the orbiting scroll 6. The lubricating oil stored in the storage section is guided to the load area A1 so as to accompany the orbiting scroll 6. Therefore, in this modified example, the distance traveled by the lubricating oil is shorter than when the storage section is provided further rearward in the orbiting direction than the midpoint C. This allows the lubricating oil to be suitably guided to the load area A1. This allows the impact generated when the ring hole 52 and the ring 33 come into contact in the load area A1 to be suitably alleviated. This allows the noise caused by the contact between the ring hole 52 and the ring 33 to be more suitably suppressed.

[0037] The present disclosure is not limited to the inventions according to the above-described embodiments, and various modifications are possible within the scope of the present disclosure. For example, in each of the above embodiments, an example has been described in which the electric compressor 1 is an inverter-integrated electric compressor, but the present disclosure is not limited to this. For example, the electric compressor 1 may be an electric compressor that does not include an inverter. Furthermore, the electric compressor 1 may be an electric compressor in which the inverter is separately installed.

[0038] Furthermore, the shape of the storage portions 41 and 51 is not limited to the shapes described above, and may be, for example, an oval shape or an elliptical shape in plan view.

[0039] In addition, in each of the above embodiments, an example has been described in which the ring hole 32 is formed in the orbiting scroll 6 and the pin 34 is fixed to the first housing 3, but the present disclosure is not limited to this. For example, the ring hole 32 may be formed in the first housing 3 and the pin 34 may be fixed to the orbiting scroll 6.

[0040] The compressor according to the above-described embodiment can be understood, for example, as follows. A compressor according to one embodiment of the present disclosure comprises a housing (2) forming an outer shell, a fixed scroll (5) accommodated in the housing and fixed to the housing side, an orbiting scroll (6) that meshes with the fixed scroll and orbits relative to the fixed scroll, a rotation-preventing mechanism (30) that prevents the orbiting scroll from rotating on its own axis, and a lubricating oil supply unit that supplies lubricating oil to the rotation-preventing mechanism, wherein the rotation-preventing mechanism has a recess (32) formed on either the orbiting scroll side or the housing side, a ring (33) that is disposed within the recess and whose outer peripheral surface (33b) faces an inner peripheral surface (32a) of the recess, and a pin (34) that is provided on the other of the orbiting scroll side or the housing side and engages with the inner peripheral surface (33a) of the ring, and a gap formed between the inner peripheral surface of the recess and the outer peripheral surface of the ring is 0.1 mm or more and 0.6 mm or less.

[0041] In the above configuration, the gap formed between the recess and the ring is 0.1 mm or more and 0.6 mm or less. This allows the lubricating oil supplied from the lubricating oil supply unit to the rotation-preventing mechanism to easily flow into the gap formed between the recess and the ring. The lubricating oil that flows into the gap reduces the impact when the recess and the ring come into contact. Therefore, noise caused by contact between the recess and the ring can be suppressed. Noise caused by contact between the recess and the ring is, for example, noise that occurs when there are multiple combinations of pins and rings and the rotation prevention function is transferred from one pin and ring combination to another pin and ring combination (when the pin and ring that perform the rotation prevention function are switched).

[0042] In the compressor according to one aspect of the present disclosure, the outer diameter of the ring is equal to or greater than 13 mm and equal to or less than 15.5 mm.

[0043] In the compressor according to the aspect of the present disclosure, the recessed portion has a reservoir portion (41, 51) formed in the inner circumferential surface, which is a cylindrical surface, and recessed radially outward.

[0044] In the above configuration, the lubricating oil supplied from the lubricating oil supply unit to the rotation-preventing mechanism is TomeThe lubricating oil is stored in the reservoir. Since the reservoir is formed on the inner peripheral surface of the recess, when the amount of lubricating oil held in the gap between the inner peripheral surface of the recess and the outer peripheral surface of the ring becomes low, the lubricating oil stored in the reservoir is guided into the gap. Therefore, the lubricating oil is more suitably held in the gap between the inner peripheral surface of the recess and the outer peripheral surface of the ring. This makes it possible to further suppress noise caused by contact between the recess and the ring.

[0045] Furthermore, a compressor according to one embodiment of the present disclosure includes a housing (2) forming an outer shell, a fixed scroll (5) accommodated in the housing and fixed to the housing side, an orbiting scroll (6) that meshes with the fixed scroll and orbits relative to the fixed scroll, a rotation-preventing mechanism (30) that prevents the orbiting scroll from rotating, and a lubricating oil supply unit that supplies lubricating oil to the rotation-preventing mechanism, wherein the rotation-preventing mechanism includes a recess (32) formed on either the orbiting scroll side or the housing side, a ring (33) that is disposed within the recess and whose outer peripheral surface (33b) faces an inner peripheral surface (32a) of the recess, and a pin (34) that is provided on the other of the orbiting scroll side or the housing side and engages with the inner peripheral surface (33a) of the ring, and the recess has a reservoir portion (41, 51) that is recessed radially outward in the inner peripheral surface, which is a cylindrical surface.

[0046] In the above configuration, the lubricating oil supplied from the lubricating oil supply unit to the rotation-preventing mechanism is stored in the oil reservoir. Because the reservoir is formed on the inner circumferential surface of the recess, when the amount of lubricating oil held in the gap between the inner circumferential surface of the recess and the outer circumferential surface of the ring becomes low, the lubricating oil stored in the reservoir is guided into the gap. This makes it easier for the lubricating oil to be held in the gap between the inner circumferential surface of the recess and the outer circumferential surface of the ring. The lubricating oil that flows into the gap cushions the impact when the recess and the ring come into contact. This reduces noise caused by contact between the recess and the ring.

[0047] In addition, in a compressor according to one embodiment of the present disclosure, the rotation prevention mechanism has a plurality of rotation prevention structures which are combinations of the recess, the ring, and the pin, and the plurality of rotation prevention structures are arranged so as to receive loads in sequence as the orbiting scroll rotates, and the inner surface of the recess of each rotation prevention structure has a load region (A1) spanning a predetermined angular range in which the inner surface receives loads from the pin as the orbiting scroll rotates, and the storage section is provided in a region (A2) of the inner surface of the recess other than the load region.

[0048] If a storage portion is formed in the load region, the load from the pin due to the orbiting motion of the orbiting scroll may cause the ring to be deformed and pushed into the storage portion. The storage portion itself may also be damaged by the load from the pin. In contrast, the above configuration has a storage portion formed in an area other than the load region. This prevents deformation and damage to the ring. Furthermore, damage to the storage portion may be prevented.

[0049] In the compressor according to one aspect of the present disclosure, the storage portion is provided forward in the orbiting direction of the orbiting scroll of a circumferential midpoint (C) of the region other than the load region.

[0050] The lubricating oil stored in the storage section is guided to the load region so as to accompany the orbiting scroll. In the above configuration, the storage section is located forward of the circumferential midpoint of the region other than the load region in the orbiting direction of the orbiting scroll. This shortens the distance traveled by the lubricating oil compared to when the storage section is located rearward of the midpoint in the orbiting direction. Therefore, the lubricating oil can be suitably guided to the load region. Therefore, the impact when the recess and the ring come into contact in the load region can be suitably alleviated. Therefore, noise caused by contact between the recess and the ring can be suppressed. [Explanation of symbols]

[0051] 1: Electric compressor (compressor) 2: Housing 3: 1st housing 4: Second housing 5: Fixed scrolling 6: Rotating scroll 6a: End plate 6b: Back 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 part 25: Inverter housing 30: Rotation prevention mechanism 31: Pin-ring structure (anti-rotation structure) 32: Ring hole (recess) 32a: Inner peripheral surface 33: Ring 33a: Inner peripheral surface 33b: Outer surface 34: Pin 41: Storage section 42: Ring hole 42a: Inner surface 51: Storage section 52: Ring hole A1:Load area A2: Anti-load area C: Midpoint G: Gap

Claims

1. a housing forming an outer shell and having a suction port through which low-pressure refrigerant gas from a refrigeration cycle is received; a fixed scroll housed in the housing and fixed to the housing; an orbiting scroll that meshes with the fixed scroll and orbits relative to the fixed scroll; a rotation prevention mechanism that prevents the orbiting scroll from rotating on its axis; a lubricant oil supply unit that supplies lubricant oil to the rotation-preventing mechanism, the rotation-preventing mechanism includes a recess formed on one of the orbiting scroll side and the casing side, a ring disposed in the recess and having an outer peripheral surface facing an inner peripheral surface of the recess, and a pin provided on the other of the orbiting scroll side and the casing side and engaging with the inner peripheral surface of the ring, a gap is formed between the inner circumferential surface of the recess and the outer circumferential surface of the ring, the gap has a longest length of 0.1 mm or more and 0.6 mm or less when a part of the outer peripheral surface of the ring is in contact with the inner peripheral surface of the recess, thereby having a function of suppressing noise generated by contact between the recess and the ring, a compressor that compresses the low-pressure refrigerant gas from the refrigeration cycle;

2. 2. The compressor according to claim 1, wherein the outer diameter of the ring is equal to or greater than 13 mm and equal to or less than 15.5 mm.

3. 3. The compressor according to claim 1, wherein the recessed portion is a reservoir portion recessed radially outward in the inner circumferential surface, which is a cylindrical surface.

4. a housing forming an outer shell; a fixed scroll housed in the housing and fixed to the housing; an orbiting scroll that meshes with the fixed scroll and orbits relative to the fixed scroll; a rotation prevention mechanism that prevents the orbiting scroll from rotating on its axis; a lubricant oil supply unit that supplies lubricant oil to the rotation-preventing mechanism, the rotation-preventing mechanism includes a recess formed on one of the orbiting scroll side and the casing side, a ring disposed in the recess and having an outer peripheral surface facing an inner peripheral surface of the recess, and a pin provided on the other of the orbiting scroll side and the casing side and engaging with the inner peripheral surface of the ring, The recessed portion is a storage portion recessed radially outwardly in the inner circumferential surface, which is a cylindrical surface.

5. the rotation-preventing mechanism has a plurality of rotation-preventing structures each of which is a combination of the recess, the ring, and the pin; the plurality of rotation-preventing structures are arranged to receive a load in sequence in accordance with the orbiting motion of the orbiting scroll, the inner circumferential surface of the recess of each rotation-preventing structure has a load region over a predetermined angular range in which the inner circumferential surface receives a load from the pin in association with the orbiting motion of the orbiting scroll, The compressor according to claim 3 or 4, wherein the reservoir portion is provided in a region of the inner circumferential surface of the recess other than the load region.

6. The compressor according to claim 5 , wherein the storage portion is provided forward in the orbiting direction of the orbiting scroll from a circumferential midpoint of the region other than the load region.

Images