Compressor and refrigeration device

Abstract

A compressor (10) is provided with a housing (20) having a cylindrical body section (20a), a member to be fixed (F) fixed to the body section (20a), and a plurality of welded sections (80) provided in the circumferential direction of the body section (20a), the plurality of welded sections (80) connecting the body section (20a) and the member to be fixed (F). The relationship between the inner diameter of the body section (20a) and the outer diameter of the member (F) to be fixed in a rated operating state of the compressor (10) corresponds to a combination (hole / shaft) H8 / f7, F8 / h9, H7 / f7, F8 / h6, H7 / g6, or G7 / h6 of a tolerance level of a hole and a tolerance level of a shaft specified in ISO 286.

Description

Technical Field

[0001] The present disclosure relates to a compressor and a refrigeration device. Background Art

[0002] Patent document 1 discloses a scroll compressor, which includes a housing, a compression mechanism, and a fixed component that supports a crankshaft (drive shaft) connected to the compression mechanism. The compression mechanism has a fixed scroll and a movable scroll (orbiting scroll) that meshes with the fixed scroll. The fixed component has a crimping portion that is crimped to the housing, and a relative portion that is opposite to the housing at a position separated from the crimping portion with a gap. In the scroll compressor of patent document 1, the relative portion of the fixed component is welded to the housing.

[0003] Prior art literature

[0004] Patent Literature

[0005] Patent Document 1: Japanese Patent Publication No. 2017-25762 Summary of the invention

[0006] -Technical problem to be solved by the invention-

[0007] In the scroll compressor of Patent Document 1, the movable scroll is connected to the crankshaft and is clamped by the fixed scroll and the fixing member. Therefore, the vibration generated in the compression mechanism during the operation of the scroll compressor is transmitted to the housing via the crankshaft and the fixing member. There is a problem that the radiated sound (noise) generated from the scroll compressor increases when the vibration is transmitted to the housing.

[0008] An object of the present disclosure is to reduce the noise of a compressor.

[0009] -Technical solutions for solving technical problems-

[0010] The first aspect is directed to a compressor 10. The compressor 10 includes a housing 20, a fixing target component F, and a plurality of welds 80. The housing 20 has a cylindrical body 20a. The fixing target component F is accommodated in the housing 20 and fixed to the body 20a. A plurality of welds 80 are provided in the circumferential direction of the body 20a, and the plurality of welds 80 connect the body 20a and the fixing target component F. The fixing target component F is a support component B that supports a compression mechanism 40 that compresses refrigerant or supports a drive shaft 11 connected to the compression mechanism 40 so that it can rotate. The relationship between the inner diameter of the body 20a and the outer diameter of the fixing target component F in the rated operation state of the compressor 10 is a matching relationship corresponding to a combination of a hole tolerance grade and a shaft tolerance grade (hole / shaft) H8 / f7, F8 / h9, H7 / f7, F8 / h6, H7 / g6, or G7 / h6 specified in ISO286.

[0011] In the first aspect, the trunk 20a of the shell 20 is fixed to the fixed object part F by a welding portion. Under the rated operation state of the compressor 10, as the pressure of the refrigerant in the shell 20 rises, the trunk 20a will expand, and the inner diameter of the trunk 20a and the outer diameter of the fixed object part F will become the above-mentioned matching relationship specified in ISO286. In this matching relationship, a local gap is generated between the trunk 20a and the fixed object part F. At this time, the fixed object part F can make a small relative movement relative to the shell 20. As a result, the energy of the vibration transmitted from the compression mechanism 40 to the fixed object part F as the compressor 10 runs is converted into kinetic energy generated by the movement of the fixed object part F or heat energy generated by the friction between the fixed object part F and the shell 20, so that the vibration transmitted from the compression mechanism 40 is attenuated. As a result, the noise generated in the compressor 10 can be reduced.

[0012] The second aspect is that, based on the first aspect, the relationship between the inner diameter of the trunk 20a in the assembled state of the compressor 10 and the outer diameter of the fixed object component F corresponds to the matching relationship of the combination of the tolerance grade of the hole and the tolerance grade of the shaft (hole / shaft) H7 / n6, H7 / r6, H7 / s6, H8 / u8 specified in ISO286.

[0013] In the second aspect, when the compressor 10 is assembled, the inner diameter of the body 20a and the outer diameter of the fixing object component F are in the above-mentioned fitting relationship specified in ISO286, so the fixing object component F is fixed to the body 20a through the welding portion 80 and the fitting.

[0014] A third aspect is a main bearing housing 50 according to the first aspect or the second aspect, and the main bearing housing 50 is used as the support member B and supports the compression mechanism 40. The compression mechanism 40 includes a fixed scroll 60 and an orbiting scroll 70 meshing with the fixed scroll 60. The fixed object member F is the main bearing housing 50.

[0015] In the third aspect, the fixing object component F is the main bearing housing 50 of the scroll compressor 10. Since the main bearing housing 50 supports the compression mechanism 40, the vibration of the compression mechanism 40 is easily transmitted to the main bearing housing 50. By applying the above-mentioned matching relationship specified in ISO286 to the inner diameter of the body portion 20a and the outer diameter of the main bearing housing 50, the noise of the compressor can be reduced.

[0016] According to a fourth aspect, in any one of the first to third aspects, in the welding portion 80 , the body portion 20 a and the fixing target member F are welded via a pin 81 .

[0017] A fifth aspect is a refrigeration device including the compressor (10) according to any one of the first to fourth aspects, and a refrigerant circuit (1a) through which the refrigerant compressed by the compressor (10) flows.

[0018] In the fifth aspect, it is possible to provide the refrigeration device 1 in which the noise of the compressor 10 is reduced. BRIEF DESCRIPTION OF THE DRAWINGS

[0019] Figure 1 1 is a refrigerant circuit diagram showing the structure of the refrigeration device of the present embodiment;

[0020] Figure 2 is a longitudinal sectional view showing the structure of a scroll compressor;

[0021] Figure 3 is Figure 2 A cross-sectional view taken along the arrow direction at line III-III;

[0022] Figure 4 is an enlarged view of the vicinity of the contact area in the assembled state of the scroll compressor;

[0023] Figure 5 It is equivalent to the rated operating state of the scroll compressor. Figure 3 's picture;

[0024] Figure 6 is a term indicating a fitting relationship, a tolerance grade specified in ISO286 corresponding to the fitting relationship, and a reference dimension corresponding to the tolerance grade. Table of dimensional tolerance ranges when

[0025] Figure 7 It is a transverse cross-sectional view showing the auxiliary bearing according to Modification 1. DETAILED DESCRIPTION

[0026] (Implementation Method)

[0027] The following is a detailed description of the embodiments of the present disclosure with reference to the accompanying drawings. It should be noted that the present disclosure is not limited to the embodiments shown below, and various changes can be made without departing from the technical concept of the present disclosure. The drawings are used to conceptually illustrate the present disclosure, so in order to facilitate understanding, the size, ratio or quantity is sometimes exaggerated or simplified as needed.

[0028] (1) Overview of Refrigeration Equipment

[0029] like Figure 1 As shown, the compressor 10 is provided in the refrigeration device 1. The refrigeration device 1 has a refrigerant circuit 1a filled with refrigerant. The refrigerant circuit 1a has the compressor 10, the radiator 3, the decompression mechanism 4 and the evaporator 5. The decompression mechanism 4 is, for example, an expansion valve. The refrigerant circuit 1a performs a vapor compression refrigeration cycle.

[0030] The refrigeration device 1 is an air conditioning device. The air conditioning device may also be a dedicated refrigeration machine, a dedicated heating machine, or an air conditioning device that switches between refrigeration and heating. In this case, the air conditioning device has a switching mechanism (such as a four-way reversing valve) that switches the circulation direction of the refrigerant. The refrigeration device 1 may also be a water heater, a cooling unit, a cooling device that cools the air in a warehouse, etc. The cooling device cools the air inside a cold storage, a freezer, a container, etc.

[0031] (2) Compressor

[0032] The compressor 10 of this embodiment is a scroll compressor. Figure 2 As shown, the scroll compressor 10 includes a housing 20, a motor 30, a drive shaft 11, and a compression mechanism 40. The housing 20 accommodates the motor 30, the drive shaft 11, and the compression mechanism 40.

[0033] It should be noted that, in the following description, "axial direction" refers to the direction in which the drive shaft 11 extends, "radial direction" refers to the direction orthogonal to the axis of the drive shaft 11, and "circumferential direction" refers to the circumferential direction based on the axis of the drive shaft 11. "Radially inner side" refers to the side close to the axis of the drive shaft 11, and "radially outer side" refers to the side away from the axis of the drive shaft 11.

[0034] (2-1) Shell

[0035] The housing 20 is formed of a sealed container having a long longitudinal length. The housing 20 has a cylindrical body 20a extending in the vertical direction and two covers 20b closing both ends of the body 20a. When the body 20a is viewed from the axial direction, the body 20a is in a non-perfect circular shape.

[0036] An oil reservoir 21 is provided at the bottom of the housing 20. Lubricating oil is stored in the oil reservoir 21. A suction pipe 12 is connected to the upper portion of the housing 20. A discharge pipe 13 is connected to the trunk 20a of the housing 20.

[0037] (2-2) Electric motor

[0038] The motor 30 has a stator 31 and a rotor 32. The stator 31 is fixed to the inner peripheral surface of the housing 20. The rotor 32 is arranged inside the stator 31. The drive shaft 11 penetrates the rotor 32. The rotor 32 is fixed to the drive shaft 11.

[0039] (2-3) Drive shaft

[0040] The drive shaft 11 extends in the up-down direction along the central axis of the housing 20. The drive shaft 11 includes a main shaft portion 14 and an eccentric portion 15.

[0041] The eccentric portion 15 is provided at the upper end of the main shaft portion 14. The outer diameter of the eccentric portion 15 is smaller than the outer diameter of the main shaft portion 14. The axis of the eccentric portion 15 is offset from the axis of the main shaft portion 14 by a predetermined distance.

[0042] The upper portion of the main shaft portion 14 passes through a fixing member 50 described below, and is rotatably supported by an upper bearing 51 of the fixing member 50. The lower portion of the main shaft portion 14 is rotatably supported by a sub-bearing 22 described below.

[0043] (2-4) Fixed parts

[0044] The housing 20 accommodates a fixing member 50. The fixing member 50 is a main bearing support member that rotatably supports the drive shaft 11. The fixing member 50 corresponds to the support member B of the present disclosure, and corresponds to the main bearing shell of the present disclosure.

[0045] The fixing member 50 is disposed below the compression mechanism 40. The fixing member 50 supports the compression mechanism 40. The fixing member 50 is disposed above the motor 30. Between the fixing member 50 and the motor 30, an inflow end of the discharge pipe 13 is disposed.

[0046] The fixing member 50 is formed into a cylindrical shape extending in the axial direction (vertical direction). The outer diameter of the upper portion of the fixing member 50 is formed to be larger than the outer diameter of the lower portion of the fixing member 50. The inner diameter of the upper portion of the fixing member 50 is formed to be larger than the inner diameter of the lower portion of the fixing member 50.

[0047] The fixed component 50 has an annular portion 52, a recessed portion 53, and an upper bearing 51. The annular portion 52 is provided at the outer periphery of the fixed component 50. When viewed from the axial direction, the annular portion 52 is non-circular. The recessed portion 53 is formed in the upper central portion of the fixed component 50. The center of the recessed portion 53 is formed into a disk shape that is recessed downward. The recessed portion 53 constitutes a crank chamber 54, and the crank chamber 54 accommodates the flange portion 73 of the orbiting scroll 70 described later.

[0048] The eccentric portion 15 rotates eccentrically in the crank chamber 54. The upper bearing 51 is formed on the lower side of the fixed member 50. Specifically, the upper bearing 51 is formed below the recess 53. A bushing 51a is fitted into the inner periphery of the upper bearing 51. The upper bearing 51 rotatably supports the main shaft portion 14 of the drive shaft 11 via the bushing 51a.

[0049] like Figure 3 As shown, a cutout portion 55 is formed on the outer peripheral surface of the annular portion 52. The cutout portion 55 penetrates the annular portion 52 in the up-down direction. The cutout portion 55 is recessed radially inward. A discharge passage 56 is formed between the cutout portion 55 and the inner peripheral surface of the shell 20 for the gaseous refrigerant discharged from the compression mechanism 40 to pass through.

[0050] The fixing member 50 is fixed inside the housing 20. Specifically, the outer peripheral surface of the annular portion 52 of the fixing member 50 is fixed to the inner peripheral surface of the body portion 20a of the housing 20. The fixing structure of the fixing member 50 will be described later.

[0051] (2-5) Compression mechanism

[0052] The compression mechanism 40 includes a fixed scroll 60 and an orbiting scroll 70. The fixed scroll 60 is fixed to an upper surface of the stationary member 50. The orbiting scroll 70 is disposed between the fixed scroll 60 and the stationary member 50.

[0053] (2-5-1) Stationary Scroll

[0054] The fixed scroll 60 includes a fixed-side end plate 61, a fixed-side wrap 62, and an outer peripheral wall 63. The fixed-side end plate 61 is formed in a disk shape.

[0055] The stationary scroll 62 is formed in a spiral shape. The stationary scroll 62 extends from the front surface ( Figure 2 The stationary scroll 62 is arranged on the inner side of the outer peripheral wall 63 of the stationary end plate 61.

[0056] The outer peripheral wall 63 is formed in a substantially cylindrical shape. The outer peripheral wall 63 extends from the front surface ( Figure 2 The outer edge of the outer wall 63 is arranged to surround the outer peripheral side of the stationary scroll 62. The front end surface ( Figure 2 The bottom of the outer wall 63 and the front end surface of the outer wall 63 ( Figure 2 ) are located at approximately the same height.

[0057] The fixed-side end plate 61 is located on the outer peripheral side and is formed to be connected to the fixed-side wrap 62. The front end surface of the fixed-side wrap 62 is formed to be substantially flush with the front end surface of the outer peripheral wall 63. The fixed scroll 60 is fixed to the fixing member 50.

[0058] (2-5-2) Orbiting Scroll

[0059] The orbiting scroll 70 includes an orbiting end plate 71, an orbiting lap 72, and a flange 73. The orbiting end plate 71 is formed in a disk shape. The orbiting lap 72 is formed in a spiral shape. The orbiting lap 72 extends from the front surface ( Figure 2 The orbiting scroll 72 meshes with the stationary scroll 62.

[0060] The flange portion 73 is formed on the back side ( Figure 2 The eccentric portion 15 of the drive shaft 11 is inserted into the flange portion 73. Thus, the drive shaft 11 is connected to the orbiting scroll 70. In other words, the drive shaft 11 is connected to the compression mechanism 40.

[0061] (2-5-3) Inlet and outlet

[0062] A suction port 64 is formed in the outer peripheral wall 63 of the fixed scroll 60. The suction port 64 opens near the winding end of the fixed scroll 62. The suction port 64 is connected to the downstream end of the suction pipe 12.

[0063] A discharge port 65 is formed at the center of the stationary end plate 61 of the stationary scroll 60. The discharge port 65 opens on the upper surface of the stationary end plate 61 of the stationary scroll 60. The high-pressure gas refrigerant discharged from the discharge port 65 flows into the lower space 24 of the stationary member 50 through the discharge passage 56 formed in the stationary member 50.

[0064] (2-5-4) Fluid Chamber

[0065] The compression mechanism 40 has a fluid chamber S into which the refrigerant flows. The fluid chamber S is formed between the fixed scroll 60 and the orbiting scroll 70. The orbiting-side lap 72 of the orbiting scroll 70 is arranged to mesh with the fixed-side lap 62 of the fixed scroll 60. The gaseous refrigerant is compressed in the fluid chamber S by the engagement of the fixed-side lap 62 with the orbiting-side lap 72.

[0066] (2-6) Crosshead coupling

[0067] An Oldham coupling 45 is provided on the upper portion of the fixed member 50. The Oldham coupling 45 is disposed between the fixed member 50 and the orbiting scroll 70. The Oldham coupling 45 prevents the orbiting scroll 70 from rotating while orbiting.

[0068] (2-7) Auxiliary bearing

[0069] The auxiliary bearing 22 is an auxiliary bearing support member that supports the drive shaft 11 so that it can rotate. The auxiliary bearing 22 is provided at the end portion ( Figure 2 The auxiliary bearing 22 is supported by the lower end portion of the auxiliary bearing 22. A bearing bush 23 is fitted into the inner periphery of the upper portion of the auxiliary bearing 22. The auxiliary bearing 22 supports the main shaft portion 14 of the drive shaft 11 via the bearing bush 23 so that it can rotate. The auxiliary bearing 22 is accommodated in the housing 20. The auxiliary bearing 22 is arranged on the side of the motor 30 opposite to the fixing member 50. In the present embodiment, the auxiliary bearing 22 is arranged below the motor 30.

[0070] The auxiliary bearing 22 is fixed inside the housing 20. Specifically, the outer peripheral surface of the auxiliary bearing 22 is fixed to the inner peripheral surface of the body 20a. The auxiliary bearing 22 is welded to the body 20a via the welding pin 81 and the joint 82. In this embodiment, the housing 20 and the auxiliary bearing 22 are not fixed by fitting.

[0071] (2-8) Oil supply line

[0072] An oil supply passage 16 is formed inside the drive shaft 11. The oil supply passage 16 extends from the lower end of the drive shaft 11 to the upper end in the vertical direction. A pump 25 is connected to the lower end of the drive shaft 11. The pump 25 is, for example, a positive displacement pump. The lower end of the pump 25 is immersed in the oil storage portion 21.

[0073] The pump 25 sucks up the lubricating oil from the oil reservoir 21 as the drive shaft 11 rotates, and delivers the lubricating oil to the oil supply passage 16. The oil supply passage 16 supplies the lubricating oil in the oil reservoir 21 to the sliding surface between the auxiliary bearing 22 and the drive shaft 11, the sliding surface between the upper bearing 51 and the drive shaft 11, and the sliding surface between the flange portion 73 and the drive shaft 11. The oil supply passage 16 opens on the upper end surface of the drive shaft 11, and supplies the lubricating oil to the upper side of the drive shaft 11.

[0074] (3) Operation of the compressor

[0075] The operation of the scroll compressor 10 will be described.

[0076] (3-1) Flow of refrigerant

[0077] exist Figure 2In the embodiment, when the motor 30 is operated, the drive shaft 11 is driven to rotate. The orbiting scroll 70 orbits along with the rotation of the drive shaft 11. Here, since the Oldham coupling 45 prevents the orbiting scroll 70 from rotating, the movable scroll 70 rotates eccentrically around the axis of the drive shaft 11.

[0078] When the orbiting scroll 70 orbits, the refrigerant flowing into the suction port 64 through the suction pipe 12 is compressed in the fluid chamber S. The high-pressure gas refrigerant compressed in the fluid chamber S is ejected from the ejection port 65 and flows into the lower space 24 through the ejection passage 56 formed in the fixed member 50. The high-pressure gas refrigerant in the lower space 24 is ejected to the outside of the shell 20 through the ejection pipe 13.

[0079] (3-2) Lubricating oil flow

[0080] As the drive shaft 11 rotates, the high-pressure lubricating oil in the oil reservoir 21 is sucked up by the pump 25 and flows upward in the oil supply passage 16 of the drive shaft 11 , and flows out from the upper end opening of the eccentric portion 15 of the drive shaft 11 into the interior of the flange portion 73 of the orbiting scroll 70 .

[0081] The lubricating oil supplied to the flange portion 73 flows out into the recessed portion 53 of the fixing member 50 through the gap between the eccentric portion 15 of the drive shaft 11 and the flange portion 73 .

[0082] The lubricating oil accumulated in the recessed portion 53 is supplied to the sliding surface between the fixed scroll 60 and the orbiting scroll 70 via an oil passage (not shown) formed in the stationary member 50 and the fixed scroll 60 , and then returns to the oil reservoir 21 .

[0083] (4) Fixing structure of fixed parts

[0084] The fixing structure of the fixing member 50 will be described.

[0085] In the present embodiment, the fixing member 50 corresponds to the fixing target member F of the present disclosure. The fixing target member F is accommodated in the housing 20 and fixed to the body portion 20 a of the housing 20 .

[0086] like Figure 3 As shown, the fixing member 50 has a contact area A that contacts the inner peripheral surface of the body 20a of the housing 20. The contact area A is formed on the outer peripheral surface of the annular portion 52 of the fixing member 50. The contact area A of the fixing member 50 is an area on the outer peripheral surface of the annular portion 52 excluding the cutout portion 55. When viewed from the axial direction, the contact area A of the fixing member 50 is formed in an arc shape. In other words, the fixing member 50 of the present embodiment has one contact area A. The fixing member 50 is fixed to the housing 20 at the contact area A by welding and fitting.

[0087] (4-1) Welding section

[0088] like Figure 2 and Figure 3 As shown, the scroll compressor 10 has a plurality of (four in this embodiment) welding portions 80 connecting the trunk 20a and the fixing member 50. In the welding portion 80, the trunk 20a and the fixing member 50 are fixed via a welding pin 81 and a joint portion 82. The welding portion 80 is formed by pressing the welding pin 81 into a hole formed in the fixing member 50 while the fixing member 50 is fixed to the housing 20, and welding the welding pin 81 to the trunk 20a. The joint portion 82 is a portion formed by melting the welding pin 81 and the trunk 20a along with welding.

[0089] like Figure 3 As shown, the welding parts 80 are arranged at predetermined intervals along the circumferential direction of the trunk 20a. In other words, four welding parts 80 are arranged circumferentially in one contact area A. As such, since the scroll compressor 10 has a plurality of welding parts 80 arranged circumferentially, it is possible to suppress the position of the fixing member 50 from being relatively offset relative to the housing 20.

[0090] (4-2) Coordination

[0091] The outer diameter of the annular portion 52 of the fixing member 50 and the inner diameter of the body portion 20 a of the housing 20 form a fitting relationship, so that the fixing member 50 is held by the housing 20 .

[0092] Here, in the scroll compressor 10 of the present embodiment, the matching relationship between the outer diameter of the fixing member 50 and the inner diameter of the housing 20 is different in the assembled state and the rated operation state of the scroll compressor 10. For the matching relationship between the outer diameter of the fixing member 50 and the inner diameter of the housing 20 in the assembled state and the rated operation state of the scroll compressor 10, refer to Figure 4 and Figure 5 Provide a detailed description.

[0093] It should be noted that the "assembled state" referred to here refers to a state in which the scroll compressor 10 is not connected to the refrigerant circuit 1a and the pressure in the shell 20 is equal to the atmospheric pressure. In addition, the "rated operating state" referred to here refers to a state in which the scroll compressor 10 is connected to the refrigerant circuit 1a and the scroll compressor 10 is operated under rated conditions.

[0094] The rated conditions here refer to the rated conditions specified in ISO5151 and JIS B 8615. The high pressure in the housing 20 under the rated conditions varies depending on the type of refrigerant filled in the refrigerant circuit 1a. For example, when the refrigerant is R32, the high pressure under the rated conditions is 2.7 MPaG or more and 3.4 MPaG or less. When the refrigerant is R410A, the high pressure under the rated conditions is 2.6 MPaG or more and 3.3 MPaG or more.

[0095] However, in each matching relationship, the dimensional tolerances of the shaft and hole in the matching relationship relative to the reference dimensions of the shaft and hole are different. Here, the reference dimension refers to the nominal size in ISO286-1:2010. In this embodiment, the reference dimensions of the outer diameter of the annular portion 52 and the inner diameter of the trunk portion 20a are The refrigerant filled in the refrigerant circuit 1a of the present embodiment is R32, and the thickness of the housing 20 is 4.4 mm.

[0096] Figure 4 FIG. 2 is an enlarged view showing the surroundings of the contact area A in the assembled state of the scroll compressor 10. Figure 4 As shown, in the assembled state of the scroll compressor 10, there is no gap between the inner peripheral surface of the body portion 20a and the outer peripheral surface of the annular portion 52, and the two are in contact with each other.

[0097] The relationship between the inner diameter of the body portion 20a and the outer diameter of the annular portion 52 in the assembled state of the scroll compressor 10 of the present embodiment corresponds to the combination of the tolerance class of the hole and the tolerance class of the shaft (hole / shaft) H7 / n6 specified in ISO286-1:2010 (hereinafter referred to as ISO286). In other words, in the assembled state, the tolerance class of the inner diameter of the body portion 20a corresponds to H7 among the tolerance classes of the hole specified in ISO286, and the tolerance class of the outer diameter of the annular portion 52 corresponds to n6 among the tolerance classes of the shaft specified in ISO286.

[0098] The above-mentioned fitting relationship is a so-called interference fit, which is a relationship in which the parts cannot move relative to each other.

[0099] In the present embodiment, the dimensional tolerance range of the scroll compressor 10 in the assembled state (specifically, the state in which the pressure in the housing 20 is equal to the atmospheric pressure) is 14 μm or more and 43 μm or less (14 μm to 43 μm) relative to the reference size. Specifically, the minimum allowable size in the assembled state of the present embodiment is 145.014 mm, and the maximum allowable size is 145.043 mm. This fitting relationship is equivalent to the so-called "tight fit".

[0100] Figure 5 FIG. 2 is an enlarged view showing the situation around the contact area A in the rated operation state of the scroll compressor 10. Figure 5 As shown, in the rated operation state of the scroll compressor 10 , a minute gap is formed between the inner peripheral surface of the body portion 20 a and the outer peripheral surface of the annular portion 52 .

[0101] When the scroll compressor 10 starts to operate, the gaseous refrigerant sucked into the shell 20 is compressed in the compression mechanism 40. The compressed gaseous refrigerant is ejected into the shell 20, thereby increasing the pressure in the shell 20. When the pressure in the shell 20 increases, the shell 20 expands. As a result, a small gap is formed between the inner peripheral surface of the trunk 20a and the outer peripheral surface of the annular portion 52.

[0102] It should be noted that in Figure 5 In order to make the figure easier to understand, the inner circumference of the trunk 20a and the outer circumference of the annular portion 52 are not in contact, but in fact, a local gap G is formed between the inner circumference of the trunk 20a and the outer circumference of the annular portion 52. In other words, between the inner circumference of the trunk 20a and the outer circumference of the annular portion 52, there are portions that are in contact with each other and portions that are not in contact with each other and form a small gap G. The formation of a local gap G between the inner circumference of the trunk 20a and the outer circumference of the annular portion 52 is caused by the following factors: strictly speaking, when viewed from the axial direction, the inner shape of the trunk 20a and the outer shape of the annular portion 52 are not perfect circles; sometimes the inner circumference of the trunk 20a is slightly inclined in the axial direction.

[0103] The relationship between the inner diameter of the body portion 20a and the outer diameter of the annular portion 52 in the rated operating state of the scroll compressor 10 of the present embodiment corresponds to a combination of the tolerance class of the hole and the tolerance class of the shaft (hole / shaft) H7 / g6 specified in ISO 286. In other words, in the rated operating state, the tolerance class of the inner diameter of the body portion 20a corresponds to H7 among the tolerance classes of the hole specified in ISO 286, and the tolerance class of the outer diameter of the annular portion 52 corresponds to g6 among the tolerance classes of the shaft specified in ISO 286.

[0104] The above-mentioned fitting relationship is a so-called limited sliding fit, which is a relationship in which the components can move relative to each other.

[0105] The dimensional tolerance range of the scroll compressor 10 of this embodiment under the rated operating state (specifically, when the pressure in the housing 20 is 2.5 MPa) is greater than -43 μm and less than 14 μm (-43 μm to 14 μm) relative to the reference size. Specifically, the minimum allowable dimension under the rated operating state of this embodiment is 144.957 mm, and the maximum allowable dimension is 145.014 mm. This fitting relationship is equivalent to the so-called "clearance fit". In detail, this fitting relationship is equivalent to the so-called "precision rotation fit".

[0106] As described above, when the scroll compressor 10 is changed from the assembled state to the rated operation state, the matching relationship between the inner diameter of the trunk portion 20 a and the outer diameter of the annular portion 52 changes.

[0107] As described above, in the rated operation state of the scroll compressor 10, a local gap G is formed between the inner peripheral surface of the trunk 20a and the outer peripheral surface of the annular portion 52, and a large positional deviation between the housing 20 and the fixing member 50 is suppressed by the plurality of welded portions 80 provided along the circumferential direction. Therefore, the fixing member 50 can perform a small relative movement with respect to the housing 20.

[0108] As a result, a gap G is formed between the inner circumferential surface of the trunk 20a and the outer circumferential surface of the annular portion 52, and the fixed component 50 vibrates due to the vibration transmitted from the compression mechanism 40 to the fixed component 50, thereby converting the vibration energy into kinetic energy, so that the vibration transmitted from the compression mechanism 40 is attenuated.

[0109] In addition, at the portion where the inner circumferential surface of the trunk 20a contacts the outer circumferential surface of the annular portion 52, the inner circumferential surface of the trunk 20a and the outer circumferential surface of the annular portion 52 rub against each other, thereby converting the energy of vibration into frictional heat energy, thereby attenuating the vibration transmitted from the compression mechanism 40.

[0110] As described above, in the rated operation state of the scroll compressor 10, by forming a local gap G between the inner peripheral surface of the body 20a and the outer peripheral surface of the annular portion 52, the fixing member 50 is slightly moved, thereby effectively attenuating the vibration generated by the compression mechanism 40. As a result, the noise generated in the scroll compressor 10 can be reduced.

[0111] It should be noted that the reference dimensions, dimensional tolerance ranges, types of refrigerants, and shell thickness in the present embodiment are all examples. In addition, the expansion degree of the shell 20 under the rated operation state of the scroll compressor 10 will vary depending on the type of refrigerant filled in the refrigerant circuit 1a and the thickness of the shell 20.

[0112] Here, in Figure 6 The terms indicating the fitting relationship, the tolerance grade specified in ISO286 corresponding to the fitting relationship, and the reference dimensions corresponding to the tolerance grade are shown in Dimensional tolerance range when .

[0113] like Figure 6 As shown, the relationship between the inner diameter of the trunk 20a and the outer diameter of the annular portion 52 in the assembled state of the scroll compressor 10 of this embodiment can also be a matching relationship corresponding to the combination of the tolerance grade of the hole and the tolerance grade of the shaft (hole / shaft) H7 / r6, H7 / s6 or H8 / u8 specified in ISO286.

[0114] The above-mentioned matching relationship is a matching relationship represented by a so-called positioning interference fit, an intermediate transmission fit or a press fit. These matching relationships are relationships in which the parts cannot move relative to each other. The above-mentioned matching relationship is equivalent to a so-called "tight fit".

[0115] like Figure 6 As shown, the relationship between the inner diameter of the trunk 20a and the outer diameter of the annular portion 52 under the rated operating state of the scroll compressor 10 of this embodiment can also be a matching relationship corresponding to the combination of the tolerance grade of the hole and the tolerance grade of the shaft specified in ISO286 (hole / shaft) H8 / f7, F8 / h9, H7 / f7, F8 / h6 or G7 / h6.

[0116] The above-mentioned matching relationship is a matching relationship expressed as a so-called tight rotation fit, a free sliding fit or a limited sliding fit. These matching relationships are relationships in which the parts can move relative to each other. These matching relationships are equivalent to the so-called "clearance fit".

[0117] When the inner diameter of the trunk 20a and the outer diameter of the annular portion 52 under the rated operating state of the scroll compressor 10 are in the matching relationship specified in the above-mentioned ISO286, a local gap G is formed between the inner circumferential surface of the trunk 20a and the outer circumferential surface of the annular portion 52, just like the case where the combination of the tolerance grade of the hole and the tolerance grade of the shaft (hole / shaft) specified in ISO286 is H7 / g6.

[0118] Thus, the energy of vibration transmitted from the compression mechanism 40 to the fixed member 50 along with the operation of the scroll compressor 10 is converted into kinetic energy generated by the movement of the fixed member 50 or heat energy generated by the friction between the fixed member 50 and the housing 20, thereby attenuating the vibration transmitted from the compression mechanism 40. As a result, the noise generated in the scroll compressor 10 can be reduced.

[0119] (5) Features

[0120] (5-1) Feature 1

[0121] The relationship between the inner diameter of the trunk 20a of the casing 20 and the outer diameter of the annular portion 52 of the fixing component 50 under the rated operating state of the scroll compressor 10 corresponds to the matching relationship of the combination of the tolerance grade of the hole and the tolerance grade of the shaft (hole / shaft) H8 / f7, F8 / h9, H7 / f7, F8 / h6, H7 / g6 or G7 / h6 specified in ISO286.

[0122] In the rated operation state of the scroll compressor 10, as the refrigerant pressure in the shell 20 rises, the trunk 20a expands, and the inner diameter of the trunk 20a and the outer diameter of the annular portion 52 become the above-mentioned matching relationship specified in ISO286. In this matching relationship, a local gap G is generated between the inner peripheral surface of the trunk 20a and the outer peripheral surface of the annular portion 52. At this time, the fixed component 50 can move slightly relative to the shell 20. As a result, the energy of the vibration transmitted from the compression mechanism 40 to the fixed component 50 along with the operation of the scroll compressor 10 is converted into kinetic energy generated by the movement of the fixed component 50 or heat energy generated by the friction between the fixed component 50 and the shell 20, so the vibration transmitted from the compression mechanism 40 is attenuated. As a result, the noise generated in the scroll compressor 10 can be reduced.

[0123] (5-2) Feature 2

[0124] The relationship between the inner diameter of the body 20a and the outer diameter of the annular portion 52 in the assembled state of the scroll compressor 10 corresponds to the matching relationship of the combinations of the tolerance grade of the hole and the tolerance grade of the shaft (hole / shaft) H7 / n6, H7 / r6, H7 / s6, and H8 / u8 specified in ISO286.

[0125] When the scroll compressor 10 is assembled, the inner diameter of the body 20a and the outer diameter of the annular portion 52 are in the above-mentioned matching relationship specified in ISO286, so the annular portion 52 of the fixing member 50 is fixed to the body 20a by the welding portion 80 and fitting.

[0126] Furthermore, by forming the welded portion 80 after holding the annular portion 52 of the fixing member 50 in the trunk portion 20a using the above-mentioned fitting relationship specified in ISO286, positional displacement of the fixing member 50 when forming the welded portion 80 can be suppressed, thereby improving the ease of assembly work.

[0127] (5-3) Feature 3

[0128] The fixed object component F is a fixed component 50 of the scroll compressor 10. Since the fixed component 50 supports the compression mechanism 40, the vibration of the compression mechanism 40 is easily transmitted to the fixed component 50. By applying the above-mentioned matching relationship specified in ISO286 to the inner diameter of the body 20a and the outer diameter of the fixed component 50, the noise of the compressor can be reduced.

[0129] (5-4) Feature 4

[0130] At the welding portion 80 , the body portion 20 a of the housing 20 and the annular portion 52 of the fixing member 50 are welded together via a welding pin 81 .

[0131] (5-5) Feature 5

[0132] The refrigeration device 1 includes the scroll compressor 10 of the present embodiment and a refrigerant circuit 1a through which flows the refrigerant compressed by the scroll compressor 10. Thus, the refrigeration device 1 in which the noise of the scroll compressor 10 is reduced can be provided.

[0133] (6) Modification

[0134] The above-mentioned embodiment may also adopt the following modified examples. It should be noted that, in the following description, the differences from the above-mentioned embodiment are described in principle.

[0135] (6-1) Modification 1

[0136] In the scroll compressor 10 of the present embodiment, the fixing object component F may be the auxiliary bearing 22. The auxiliary bearing 22 corresponds to the support component B of the present disclosure. Since the auxiliary bearing 22 is connected to the compression mechanism 40 via the drive shaft 11, the vibration generated by the compression mechanism 40 is transmitted to the auxiliary bearing 22 via the drive shaft 11.

[0137] Here, if Figure 7 As shown, the auxiliary bearing 22 is formed in a manner spanning the housing 20. The auxiliary bearing 22 has an annular ring portion 22a formed in the center and three protrusions 22b protruding radially outward from the annular portion. The drive shaft 11 is inserted into the center of the annular portion 22a. The three protrusions 22b are arranged at predetermined intervals in the circumferential direction.

[0138] The auxiliary bearing 22 has a plurality of (three in this modified example) contact areas A that contact the inner peripheral surface of the body portion 20a of the housing 20. The contact areas A of the auxiliary bearing 22 are formed on the outer peripheral surface of each protrusion 22b. When viewed from the axial direction, each contact area A of the auxiliary bearing 22 is formed in an arc shape.

[0139] In this modification, when the scroll compressor 10 is in a stopped state, the auxiliary bearing 22 is fixed to the housing 20 in the contact area A by welding and fitting. In this modification, three welding portions 80 are arranged at predetermined intervals along the circumference of the trunk 20a. The three welding portions 80 are respectively provided in each contact area A. In other words, one welding portion 80 is provided for one contact area A. In this way, since the scroll compressor 10 has a plurality of welding portions 80 arranged along the circumferential direction, it is possible to suppress the relative displacement of the position of the auxiliary bearing 22 relative to the housing 20.

[0140] In this variation, the relationship between the inner diameter of the body 20a of the scroll compressor 10 in the assembled state and the outer diameter of the annular portion 52 corresponds to the matching relationship of the combination of the tolerance grade of the hole and the tolerance grade of the shaft (hole / shaft) H7 / n6, H7 / r6, H7 / s6, H8 / u8 specified in ISO286.

[0141] In this variation, the relationship between the inner diameter of the trunk 20a and the outer diameter of the annular portion 52 under the rated operating state of the scroll compressor 10 corresponds to the matching relationship of the combination of the tolerance grade of the hole and the tolerance grade of the shaft (hole / shaft) H8 / f7, F8 / h9, H7 / f7, F8 / h6, H7 / g6 or G7 / h6 specified in ISO286.

[0142] Therefore, even when the fixing object component F is the auxiliary bearing 22, since a local gap G is formed between the inner peripheral surface of the body 20a of the housing 20 and the outer peripheral surface of each protrusion 22b of the auxiliary bearing 22, the same effect as the above embodiment can be obtained.

[0143] (Other embodiments)

[0144] The above-mentioned embodiment may also adopt the following structure.

[0145] The compressor 10 of the above-mentioned embodiment may also be a rotary compressor. In this case, the fixed object component F may also be a front cylinder head, a cylinder or a rear cylinder head. The cylinder is a component constituting a compression mechanism, and forms a fluid chamber together with a piston. The front cylinder head and the rear cylinder head are bearing support components that support the drive shaft so that it can rotate. The front cylinder head or the rear cylinder head corresponds to the support component B of the present disclosure. The cylinder, the front cylinder head and the rear cylinder head are formed into a cylindrical shape. The outer peripheral surface of the cylinder, the front cylinder head and the rear cylinder head is fixed to the inner peripheral surface of the shell.

[0146] In addition, when the compressor 10 of the above embodiment is a rotary compressor, the support member B may also be a mounting plate that supports the front cylinder head body on the housing. The mounting plate is a component of the front cylinder head. When the front cylinder head has a mounting plate, the front cylinder head is fixed to the housing via the mounting plate. The mounting plate is, for example, a plate-shaped member formed along the inner circumference of the housing and having a longitudinal section that is substantially L-shaped.

[0147] The above embodiments and variations are described, but it should be understood that various changes can be made to the methods and specific circumstances without departing from the spirit and scope of the claims. In addition, the above embodiments, variations, and other embodiments may be appropriately combined or replaced.

[0148] The terms "first", "second", "third", etc. mentioned above are only used to distinguish the sentences containing the above terms, and do not limit the quantity and order of the sentences.

[0149] - Industrial Applicability -

[0150] In summary, the present disclosure is very useful for compressors and refrigeration devices.

[0151] - Explanation of symbols -

[0152] 1 Refrigeration unit

[0153] 1a Refrigerant circuit

[0154] 10Compressor (Scroll compressor)

[0155] 11 Drive shaft

[0156] 20 Shell

[0157] 20a Trunk

[0158] 40 Compression mechanism

[0159] 50 Fixed component (main bearing shell)

[0160] 60 static scroll

[0161] 70 Orbital Scroll

[0162] 80 Welding Department

[0163] 81 welding pin (pin)

[0164] B Supporting parts

[0165] F Fixing target parts

Claims

1. A compressor, characterized in that: The compressor includes a housing (20), a fixing target component (F), and a plurality of welding portions (80). The housing (20) has a cylindrical body (20a). The fixing object component (F) is accommodated in the housing (20) and fixed to the trunk (20a). A plurality of the welding parts (80) are provided in the circumferential direction of the trunk part (20a), and the plurality of the welding parts (80) connect the trunk part (20a) and the fixing object component (F). The fixing object component (F) is a supporting component (B), and the supporting component (B) supports a compression mechanism (40) for compressing refrigerant or supports a drive shaft (11) connected to the compression mechanism (40) so that it can rotate. The relationship between the inner diameter of the trunk (20a) and the outer diameter of the fixed object component (F) under the rated operating state of the compressor (10) corresponds to the matching relationship of the combination of the tolerance grade of the hole and the tolerance grade of the shaft (hole / shaft) H8 / f7, F8 / h9, H7 / f7, F8 / h6, H7 / g6 or G7 / h6 specified in ISO286.

2. The compressor according to claim 1, characterized in that: The relationship between the inner diameter of the trunk (20a) and the outer diameter of the fixed object component (F) in the assembled state of the compressor (10) corresponds to the matching relationship of the combination of the tolerance grade of the hole and the tolerance grade of the shaft (hole / shaft) H7 / n6, H7 / r6, H7 / s6, H8 / u8 specified in ISO286.

3. The compressor according to claim 1 or 2, characterized in that: The compressor includes a main bearing housing (50), the main bearing housing (50) serving as the support member (B) and supporting the compression mechanism (40). The compression mechanism (40) includes a fixed scroll (60) and an orbiting scroll (70) meshing with the fixed scroll (60). The fixing target component (F) is the main bearing housing (50).

4. The compressor according to any one of claims 1 to 3, characterized in that: At the welding portion (80), the body portion (20a) and the fixing target component (F) are welded via a pin (81).

5. A refrigeration device, characterized in that: The refrigeration device comprises: The compressor (10) according to any one of claims 1 to 4; and A refrigerant circuit (1a) through which the refrigerant compressed by the compressor (10) flows.

Images