CN116157600A

CN116157600A - Scroll compressor having a rotor with a rotor shaft having a rotor shaft with a

Info

Publication number: CN116157600A
Application number: CN202180052658.5A
Authority: CN
Inventors: 安田文昭; 达胁浩平; 梅钵佑介
Original assignee: Mitsubishi Electric Corp
Current assignee: Mitsubishi Electric Corp
Priority date: 2020-09-02
Filing date: 2021-08-25
Publication date: 2023-05-23
Also published as: GB2612265B; GB2612265A; JPWO2022050142A1; DE112021004542T5; WO2022050142A1; GB202302459D0; JP7321384B2

Abstract

The 1 st part (251) and the 2 nd part (252) are provided on both left and right sides with respect to a 1 st axis (27) passing through the center of a 1 st Euclidean groove (215) of the main frame (2), the 1 st part (251) and the 2 nd part (252) are configured so as to cross the 2 nd axis (26) with respect to a 2 nd axis (26) passing through the center of the main frame (2) as a straight line perpendicular to the 1 st axis (27), and the rigidity against bending moment generated by compressive load applied in the radial direction is lower than other components of the main frame (2).

Description

Scroll compressor having a rotor with a rotor shaft having a rotor shaft with a

Technical Field

The present application relates to scroll compressors.

Background

Among the conventional scroll compressors, there is a scroll compressor having: a stator fixed to a central portion of the housing; a main frame fixed to an upper portion of the inside of the housing; and a sub-frame fixed to a lower portion of the inside of the case. The device also comprises: a crankshaft supported by a bearing fixed to the sub-frame and the main frame; a rotor fixed to the crankshaft; a swing scroll installed at an eccentric portion of a front end of the crankshaft; and a fixed scroll disposed opposite to the orbiting scroll and fixed to the housing. The crank shaft is rotated by the power of the stator and the rotor, and the orbiting scroll performs an orbiting motion with respect to the fixed scroll, thereby compressing the refrigerant in a compression chamber formed by the orbiting scroll and the fixed scroll (see patent document 1).

Prior art literature

Patent literature

Patent document 1: international publication No. 2018/078787

Disclosure of Invention

Problems to be solved by the invention

In the scroll compressor described in patent document 1, when the main frame is fixed to the 2 nd inner wall surface of the main casing by a heat press fit or the like, a load is applied to the contact surface of the outermost diameter of the main frame. As a result, stress is generated in the main frame, and the main frame is deformed. Depending on the position of the suction port or the like provided in the main frame, the stress distribution is deviated, and the flat surface of the main frame is deformed, and the flatness of the flat surface is deteriorated. Along with this, there are such problems that: the orbiting scroll supported on the flat surface of the main frame is inclined, and parallelism and a straight angle of the scrolls of the orbiting scroll and the fixed scroll are deteriorated, so that the tip clearance cannot be assembled with high accuracy. Therefore, there is a problem that: the performance of the compressor is deteriorated due to an increase in sliding resistance of the orbiting scroll, the fixed scroll, the main frame, a deterioration in air tightness, and the like. Therefore, it is necessary to suppress deterioration of the flatness of the flat surface of the main frame.

The present application discloses a technique for solving the above-described problems, and an object thereof is to provide a scroll compressor capable of suppressing deterioration of flatness of a flat surface of a main frame.

Means for solving the problems

The scroll compressor disclosed in the present application comprises: a fixed scroll having a 1 st scroll body; a orbiting scroll having a 2 nd scroll body, the 2 nd scroll body and the 1 st scroll body being engaged with each other to form a compression chamber; an Oldham ring provided with a 2 nd key portion, the 2 nd key portion being received in a pair of 2 nd Euclidean grooves provided in the orbiting scroll; a main frame provided with a pair of 1 st Euclidean grooves for receiving a pair of 1 st keys provided on the Euclidean ring; and a housing that accommodates the fixed scroll, the orbiting scroll, and the main frame on an inner side,

in the main frame, a 1 st part and a 2 nd part are provided on both left and right sides with respect to a 1 st axis passing through a center of the 1 st Euclidean groove, the 1 st part and the 2 nd part have lower rigidity against bending moment generated by compressive load applied in a radial direction than other constituent parts of the main frame, and,

the 1 st and 2 nd portions are disposed so as to cross the 2 nd axis with respect to the 2 nd axis, which is a straight line perpendicular to the 1 st axis and passes through the center of the main frame.

In addition, another scroll compressor disclosed in the present application includes: a fixed scroll having a 1 st scroll body; a orbiting scroll having a 2 nd scroll body, the 2 nd scroll body and the 1 st scroll body being engaged with each other to form a compression chamber; an Oldham ring provided with a 2 nd key portion, the 2 nd key portion being received in a pair of 2 nd Euclidean grooves provided in the orbiting scroll; a main frame provided with a pair of 1 st Euclidean grooves for receiving a pair of 1 st keys provided on the Euclidean ring; and a housing that accommodates the fixed scroll, the orbiting scroll, and the main frame on an inner side,

the main frame is provided with a portion having higher rigidity at a position corresponding to a circumferential position of a portion having lower rigidity against bending moment generated by a compressive load applied in a radial direction than other constituent portions of the main frame.

Effects of the invention

According to the scroll compressor disclosed in the present application, deterioration of flatness of the flat surface of the main frame can be suppressed.

Drawings

Fig. 1 is a perspective view showing a scroll compressor according to embodiment 1.

Fig. 2 is a longitudinal sectional view showing the scroll compressor of embodiment 1.

Fig. 3 is a perspective view showing an intermediate housing in the scroll compressor of embodiment 1.

Fig. 4 is a perspective view showing a main frame in the scroll compressor of embodiment 1.

Fig. 5 is a perspective view showing a fixed scroll in the scroll compressor of embodiment 1.

Fig. 6 is a perspective view showing an oscillating scroll in the scroll compressor of embodiment 1.

Fig. 7 is a perspective view showing an euclidean ring in the scroll compressor of embodiment 1.

Fig. 8 is a perspective view showing a crankshaft in the scroll compressor of embodiment 1.

Fig. 9 is a perspective view showing a bushing in the scroll compressor of embodiment 1.

Fig. 10 is a cross-sectional view showing the K portion in fig. 2.

Fig. 11 is an enlarged view of a portion a in fig. 10.

Fig. 12 is an enlarged view of a portion B in fig. 10.

Fig. 13 is an enlarged perspective view showing the protruding portion.

Fig. 14 is an enlarged perspective view showing the protruding portion.

Fig. 15 is a cross-sectional view showing the K portion in fig. 2.

Fig. 16 is an enlarged cross-sectional view showing the main frame and the orbiting scroll portion.

Fig. 17 is an enlarged cross-sectional view showing the main frame and the orbiting scroll portion.

Fig. 18 is an enlarged cross-sectional view showing the main frame and the orbiting scroll portion.

Fig. 19 is an enlarged cross-sectional view showing the main frame and the orbiting scroll portion.

Fig. 20 is a plan view showing the main frame.

Fig. 21 is a sectional view taken along the plane passing through the X-axis in fig. 20.

Fig. 22 is a plan view showing the main frame.

Fig. 23 is a plan view showing the main frame.

Fig. 24 is a plan view showing the main frame.

Fig. 25 is a plan view showing the main frame.

Fig. 26 is a plan view showing a main frame in the scroll compressor of embodiment 2.

Fig. 27 is a sectional view taken along the plane passing through the X-axis in fig. 26.

Fig. 28 is a sectional view showing the main frame.

Fig. 29 is a perspective view of the main frame as seen from one end side.

Fig. 30 is a perspective view of the main frame as seen from the other end side.

Fig. 31 is a plan view of the main frame as seen from the other end side.

Fig. 32 is a plan view of the main frame as seen from the other end side.

Fig. 33 is a perspective view of the main frame as seen from one end side.

Fig. 34 is a perspective view of the main frame as seen from the other end side.

Fig. 35 is a plan view of the main frame as seen from the other end side.

Fig. 36 is a plan view of the main frame as seen from the other end side.

Detailed Description

Embodiment 1

The present embodiment relates to a scroll compressor, and more particularly, to a structure of a main frame which is a constituent member of the scroll compressor.

Embodiment 1 will be described below with reference to the drawings. Fig. 1 is a perspective view showing a scroll compressor, fig. 2 is a longitudinal sectional view showing the scroll compressor, fig. 3 is a perspective view showing an intermediate housing in the scroll compressor, fig. 4 is a perspective view showing a main frame, fig. 5 is a perspective view showing a fixed scroll, and a view of the fixed scroll is seen from a lower side. Fig. 6 is a perspective view showing the orbiting scroll, fig. 6A is a perspective view showing a case where the orbiting scroll is viewed from the upper side, and fig. 6B is a perspective view showing a case where the orbiting scroll is viewed from the lower side. Fig. 7 is a perspective view showing an Oldham ring (Oldham ring), fig. 8 is a perspective view showing a crankshaft, and fig. 9 is a perspective view showing a bushing. The compressor shown in fig. 1 is a so-called vertical scroll compressor that is used in a state in which the central axis of the crankshaft is substantially perpendicular to the ground.

The scroll compressor includes a housing 1, a main frame 2, a compression mechanism 3, a drive mechanism 4, a subframe 5, a crankshaft 6, a bushing 7, and a power supply 8. In the following description, the side (upper side) where the compression mechanism portion 3 is provided is oriented to one end side and the side (lower side) where the driving mechanism portion 4 is provided is oriented to the other end side with reference to the main frame 2.

The case 1 is a case made of metal and having both ends closed, and is composed of a middle case 11, an upper case 12, and a lower case 13. The intermediate housing 11 is formed in a cylindrical shape, and its side wall is connected to the suction pipe 14 by welding or the like. The suction pipe 14 is a pipe for introducing the refrigerant into the casing 1, and communicates with the inside of the intermediate casing 11.

The upper case 12 is formed in a substantially hemispherical shape, and a part of its side wall is connected to the upper end portion of the intermediate case 11 by welding or the like, and the upper case 12 covers the upper opening portion of the intermediate case 11. The discharge pipe 15 is connected to the upper portion of the upper case 12 by welding or the like. The discharge pipe 15 is a pipe for discharging the refrigerant to the outside of the casing 1, and communicates with the inner space of the intermediate casing 11. The lower case 13 is formed in a substantially hemispherical shape, and a part of its side wall is connected to the lower end portion of the intermediate case 11 by welding or the like, and the lower case 13 covers the opening portion of the lower side of the intermediate case 11. The housing 1 is supported by a fixing base 16 having a plurality of screw holes. The fixing base 16 is formed with a plurality of screw holes, and screws are screwed into the screw holes, so that the scroll compressor can be fixed to other components such as a casing of the outdoor unit.

As shown in fig. 4, the main frame 2 is made of metal such as cast iron, is formed as a hollow frame having a hollow formed therein, and is provided in the housing 1. The main frame 2 includes a main body 21, a main bearing 22, and an oil return pipe 23. The main body 21 is fixed to an inner wall surface of one end side of the intermediate housing 11, and a storage space 211 is formed in a central portion along the longitudinal direction of the housing 1. The storage space 211 is formed in a stepped shape having one end side open and a space narrowed toward the other end side. An annular flat surface 212 is formed on one end side of the main body 21 so as to surround the accommodation space 211. An annular thrust plate 24 (see fig. 10) made of a steel plate material such as valve steel is disposed on the flat surface 212. Thus, in the present embodiment, the thrust plate 24 functions as a thrust bearing.

Further, since the thrust plate 24 functions as a thrust bearing, a rotation stopper for suppressing rotation is required. Although not shown here, for example, a protrusion thinner than the thickness of the thrust plate 24 is provided on the flat surface 212 of the main frame 2, so that the rotation of the thrust plate 24 can be suppressed. Further, the main frame 2 may be formed with a groove, and the thrust plate 24 may be formed with a projection to fit the two members. Further, a suction port 213 is formed at a position on the outer end side of the flat surface 212 of the main frame 2, which does not overlap with the thrust plate 24. The suction port 213 is a space penetrating the body 21 in the vertical direction, that is, on the upper case 12 side and the lower case 13 side. In fig. 4, although the case where 2

suction ports

213, 2 oil return pipes 23 are provided is shown, the number is not limited thereto. The suction port 213 is a through hole, but may be a slit shape with the outer wall removed.

An euclidean accommodating portion 214 is formed in a step portion of the main frame 2 on the other end side of the flat surface 212. The 1 st euclidean groove 215 is formed in the euclidean accommodating portion 214. The 1 st euclidean groove 215 is formed as a part of the outer end side cutting the inner end side of the flat surface 212. Therefore, when the main frame 2 is viewed from one end side, a part of the 1 st euclidean groove 215 overlaps the thrust plate 24. The 21 st euclidean grooves 215 constituting a pair are formed so as to face each other. The main bearing portion 22 is formed continuously with the other end side of the main body portion 21, and a shaft hole 221 is formed in the main bearing portion 22. The shaft hole 221 penetrates the main bearing portion 22 in the vertical direction, and one end side of the shaft hole 221 communicates with the accommodation space 211. The oil return pipe 23 is a pipe for returning the lubricating oil accumulated in the storage space 211 to an oil reservoir provided inside the lower case 13, and is inserted and fixed into an oil drain hole formed through the inside and outside of the main frame 2.

The lubricating oil is, for example, a refrigerating machine oil containing an ester-based synthetic oil. The lubricating oil is stored in the lower part of the casing 1, that is, in the lower casing 13, and is sucked by an oil pump 52 described later and passed through an oil passage 63 provided in the crankshaft 6, so that wear of mechanically contacted members such as the compression mechanism 3 is reduced, and the temperature of the sliding portion is adjusted, thereby further improving the sealing performance. An oil excellent in lubricating properties, electrical insulation, stability, refrigerant solubility, low-temperature fluidity, and the like and having a moderate viscosity is preferable as the lubricating oil.

The compression mechanism 3 is a compression mechanism that compresses a refrigerant. The compression mechanism 3 is a scroll compression mechanism including a fixed scroll 31 and a orbiting scroll 32. As shown in fig. 2 and 5, the fixed scroll 31 is made of metal such as cast iron, and includes a 1 st base plate 311 and a 1 st scroll 312. The 1 st substrate 311 is formed in a disk shape, and a discharge port 313 is formed penetrating in the vertical direction at the center thereof. The 1 st scroll 312 protrudes from the other end surface of the 1 st base plate 311 to form a scroll-like wall, and the tip end thereof protrudes toward the other end.

As shown in fig. 6A and 6B, the orbiting scroll 32 is made of a metal such as aluminum, and includes a 2 nd base plate 321, a 2 nd scroll 322, a cylindrical portion 323, and a 2 nd euclidean groove 324. The 2 nd base plate 321 is formed in a disk shape including one surface, the other surface, and a side surface 3212, the 2 nd scroll 322 is formed on the one surface, at least a part of an outer peripheral region of the other surface becomes a sliding surface 3211, and the side surface 3212 is located radially outermost to connect the one surface and the other surface. The sliding surface 3211 on the other surface is slidable with respect to the thrust plate 24 and is supported (supported) by the main frame 2.

The 2 nd scroll 322 protrudes from one surface of the 2 nd base plate 321 to form a scroll-like wall, and the tip end thereof protrudes toward one end side. Further, seal members for suppressing leakage of the refrigerant are provided at the tip ends of the 1 st scroll 312 of the fixed scroll 31 and the 2 nd scroll 322 of the orbiting scroll 32. The cylindrical portion 323 is a cylindrical boss formed protruding from the substantially center of the other surface of the 2 nd substrate 321 toward the other end side. A journal bearing, which is a swing bearing that rotatably supports a slider 71 described later, is provided on the inner peripheral surface of the cylindrical portion 323 so that its center axis is parallel to the center axis of the crankshaft 6.

The 2 nd euclidean groove 324 is a rectangular groove formed on the other surface of the 2 nd substrate 321, and one surface is formed in an arc shape. The 2 nd euclidean grooves 324 constituting a pair are provided so as to face each other. The line connecting the 2 nd euclidean grooves 324 constituting a pair is arranged perpendicular to the line connecting the 2 st euclidean grooves 215 constituting a pair.

The euclidean ring 33 is disposed in the euclidean housing 214 provided in the main frame 2. As shown in fig. 7, the euclidean ring 33 includes a ring portion 331, a 1 st key portion 332, and a 2 nd key portion 333. The ring portion 331 is formed in a ring shape. Of the 1 st

key portions

332, 21 st key portions 332 constituting a pair are formed on the surface of the other end side of the ring portion 331 so as to face each other, and are accommodated in 2 st euclidean grooves 215 constituting a pair of the main frame 2. Of the 2 nd

key parts

333, 2 nd key parts 333 constituting a pair are formed on one end side surface of the ring part 331 so as to face each other, and are accommodated in 2 nd euclidean grooves 324 constituting a pair of the orbiting scroll 32.

When the orbiting scroll 32 orbits by the rotation of the crankshaft 6, the 1 st key 332 slides in the 1 st euclidean groove 215, and the 2 nd key 333 slides in the 2 nd euclidean groove 324, whereby the euclidean ring 33 prevents the orbiting scroll 32 from rotating. The compression chamber 34 is formed by engaging the 1 st scroll 312 of the fixed scroll 31 and the 2 nd scroll 322 of the orbiting scroll 32 with each other. Since the volume of the compression chamber 34 decreases from the outside toward the inside in the radial direction, the refrigerant is taken in from the outer end side of the scroll and moved toward the center side, and is gradually compressed.

The compression chamber 34 communicates with the discharge port 313 at the central portion of the fixed scroll 31. A muffler 35 having a discharge hole 351 is provided on one end side of the fixed scroll 31, and a discharge valve 36 is provided, and the discharge valve 36 opens and closes the discharge hole 351 when predetermined, thereby preventing backflow of the refrigerant. The refrigerant is composed of, for example, a halogenated hydrocarbon having a carbon double bond in the component, a halogenated hydrocarbon having no carbon double bond, a hydrocarbon, and a mixture containing them. As the halogenated hydrocarbon having a carbon double bond, there are exemplified tetrafluoropropenes such as HFO1234yf, HFO1234ze, HFO1243zf represented by the chemical formula C3H2F4, for HFC refrigerants and freon-based low GWP refrigerants having zero ozone layer destruction coefficient. Examples of the halogenated hydrocarbon having no carbon double bond include a refrigerant in which R32 (difluoromethane) represented by CH2F2, R41, and the like are mixed. Examples of the hydrocarbon include propane and propylene as natural refrigerants. Examples of the mixture include mixed refrigerants in which R32, R41, and the like are mixed with HFO1234yf, HFO1234ze, HFO1243zf, and the like.

The drive mechanism 4 is provided on the other end side with respect to the main frame 2 inside the housing 1. The drive mechanism 4 includes a stator 41 and a rotor 42. The stator 41 is a stator in which a winding is wound on an iron core formed by stacking a plurality of electromagnetic steel plates, for example, with an insulating layer interposed therebetween, and is formed in a ring shape. The stator 41 is fixedly supported inside the intermediate housing 11 by a press fit or the like. The rotor 42 is a cylindrical rotor having a permanent magnet built in an iron core formed by laminating a plurality of electromagnetic steel plates and having a through hole penetrating in the vertical direction in the center, and is disposed in an inner space of the stator 41.

The sub-frame 5 is a frame made of metal such as cast iron, for example, and is provided on the other end side with respect to the drive mechanism section 4 inside the housing 1. The sub-frame 5 is fixedly supported by the inner peripheral surface of the other end side of the intermediate housing 11 by press fitting, welding, or the like. The sub-frame 5 includes a sub-bearing 51 and an oil pump 52. The sub-bearing 51 is a ball bearing provided above the center of the sub-frame 5, and has a vertically penetrating hole in the center. The oil pump 52 is provided at the lower side of the center of the sub-frame 5, and is disposed so as to be at least partially immersed in the lubricating oil stored in the oil reservoir of the casing 1. In addition, although the ball bearing is shown as the sub-bearing portion 51 in fig. 2, it may be, for example, a journal bearing.

As shown in fig. 8, the crankshaft 6 is a long rod-shaped metal member and is provided inside the housing 1. The crankshaft 6 includes a main shaft portion 61, an eccentric shaft portion 62, and an oil passage 63. The main shaft portion 61 is a shaft constituting a main portion of the crankshaft 6, and its center axis is arranged to coincide with the center axis of the intermediate housing 11. The rotor 42 is fixed in contact with the outer side surface of the main shaft portion 61. The eccentric shaft portion 62 is provided on one end side of the main shaft portion 61 such that a central axis of the eccentric shaft portion 62 is eccentric with respect to a central axis of the main shaft portion 61. The oil passage 63 is provided vertically penetrating the inside of the main shaft 61 and the eccentric shaft 62. With respect to the crankshaft 6, one end side of the main shaft portion 61 is inserted into the main bearing portion 22 of the main frame 2, and the other end side of the main shaft portion 61 is inserted into the sub-bearing portion 51 fixed to the sub-frame 5. Thus, the eccentric shaft portion 62 is disposed in the cylinder of the cylindrical portion 323 of the orbiting scroll 32. The outer peripheral surface of the rotor 42 and the inner peripheral surface of the stator 41 are disposed with a predetermined gap therebetween. Further, a 1 st balancer 64 is provided on one end side of the main shaft portion 61, and a 2 nd balancer 65 is provided on the other end side of the main shaft portion 61 to cancel unbalance caused by the swing of the swing scroll 32.

As shown in fig. 9, the bushing 7 is made of metal such as iron, and is a connecting member for connecting the orbiting scroll 32 and the crankshaft 6. In fig. 9, the bush 7 is composed of 2 parts, that is, provided with a slider 71 and a balance weight 72. The slider 71 is a cylindrical member having a flange portion formed thereon, and is fitted into the eccentric shaft portion 62 and the cylindrical portion 323, respectively. The balance weight 72 is a ring-shaped member including a weight portion 721, which is provided eccentrically with respect to the rotation center to cancel the centrifugal force of the orbiting scroll 32, and the weight portion 721 has a substantially C-shape when viewed from one end side. The balance weight 72 is fitted to the flange portion of the slider 71 by, for example, a heat press fit method. The bush 7 may be formed of 1 piece by integrally cutting the slider 71 and the balance weight 72 by machining, for example.

As shown in fig. 2 and 3, the power supply unit 8 is a power supply member for supplying power to the scroll compressor, and is formed on the outer peripheral surface of the intermediate housing 11 of the housing 1. The power supply unit 8 includes a cover 81, a power supply terminal 82, and a wiring 83. The cover 81 is a cover member having an opening and having a bottom. The power supply terminal 82 is made of a metal member, and is provided in the cover 81. One of the wires 83 is connected to the power supply terminal 82, and the other is connected to the stator 41.

Fig. 10 is a cross-sectional view showing the K portion in fig. 2. Fig. 11 is an enlarged view of a portion a in fig. 10, and fig. 12 is an enlarged view of a portion B in fig. 10. In fig. 10, the intermediate housing 11 has a 1 st protruding portion 112, and the 1 st protruding portion 112 protrudes radially from the 1 st inner wall surface 111. The intermediate housing 11 has a 1 st positioning surface 113, and the 1 st positioning surface 113 is an end surface of the 1 st projection 112 facing the upper housing 12 side, and contacts the 1 st base plate 311 of the fixed scroll 31 to determine the axial position of the fixed scroll 31. Further, the intermediate housing 11 has: a 2 nd inner wall surface 114 as an inner wall surface of the 1 st projection 112; and a 2 nd protrusion 115 further protruding radially from the 1 st protrusion 112. Further, the intermediate housing 11 has: a 2 nd positioning surface 116, which is an end surface of the 2 nd protrusion 115 facing the upper case 12 side, and which contacts the main body 21 of the main frame 2 to determine the axial position of the main frame 2; and a 3 rd inner wall surface 117 as an inner wall surface of the 2 nd protrusion 115.

That is, the intermediate housing 11 includes a stepped portion in which the inner diameter decreases toward the other end side. The 1 st positioning surface 113 and the 2 nd positioning surface 116 are formed substantially perpendicular to the central axis of the crankshaft 6, and the normal vectors of both positioning surfaces are formed to be oriented in the same direction. As shown in fig. 3, a groove 118 is formed in the 1 st projection 112, and the groove 118 is fitted into a projection 314 of the fixed scroll 31 and a projection 216 of the main frame 2 described later to determine the phases of the two members. A chamfer portion 1181, which is C-chamfered (a corner is cut out in an isosceles right triangle shape) or R-chamfered (rounded) is formed at the front end of the groove 118 on the upper case 12 side, so that the groove width gradually becomes narrower from the front end. Thus, the chamfered portion 1181 serves as a guide, and the protrusion 216 of the main frame 2 and the protrusion 314 of the fixed scroll 31 are easily guided, so that the assembly is easy, and the assembly of the compressor is improved.

Recesses

1131 and 1161 are provided at the corners where the 1 st positioning surface 113 and the 1 st inner wall surface 111 intersect and at the corners where the 2 nd positioning surface 116 and the 2 nd inner wall surface 114 intersect, respectively. This enables the fixed scroll 31 and the main frame 2 to reliably contact the positioning surfaces. In addition, in the case of manufacturing the intermediate housing 11 by using a welded steel pipe in which a plate-shaped steel material is formed into a tubular shape by rolling or pressing, and then joined by welding to form a steel pipe, if the groove 118 is formed at a portion other than the welded joint portion, the groove can be formed without impairing the reliability of the intermediate housing 11.

As shown in fig. 4, the main frame 2 has a projection 216, and the projection 216 projects radially from the outer diameter of the main body 21. Fig. 13 is an enlarged perspective view showing the protruding portion. A chamfer portion 2161, which is C-chamfered or R-chamfered, is formed at the front end of the lower case 13 side of the projection 216, and the projection width is gradually increased from the front end. The phase of the main frame 2 is determined by fitting the projection 216 into the groove 118 formed in the intermediate housing 11. Further, the main body portion 21 of the main frame 2 is brought into contact with the 2 nd positioning surface 116 formed on the intermediate housing 11, thereby determining the position in the axial direction of the main frame 2. Further, in this state, the main frame 2 is fixed to the 2 nd inner wall surface 114 or the 3 rd inner wall surface 117 of the intermediate housing 11 by press-fitting and heat press-fitting, thereby determining the center position. In addition, when the holding force is insufficient, arc spot welding or the like may be further performed. By the above operation, the main frame 2 can be held to the intermediate housing 11 in a state where the center position, the axial height position, and the phase are determined with respect to the intermediate housing 11.

As shown in fig. 5, the fixed scroll 31 has a protrusion 314, and the protrusion 314 protrudes from the side of the 1 st base plate 311 on which the 1 st scroll 312 is formed toward the lower housing 13. Fig. 14 is an enlarged perspective view showing the protruding portion. A chamfer 3141, which is C-chamfered or R-chamfered, is formed at the front end of the projection 314 on the lower case 13 side, so that the projection width gradually increases from the front end. The phase of the fixed scroll 31 is determined by fitting the protrusion 314 into the groove 118 formed in the intermediate housing 11. Further, as shown in fig. 10, the surface of the 1 st base plate 311 of the fixed scroll 31 on the side where the 1 st scroll 312 is formed is brought into contact with the 1 st positioning surface 113 formed in the intermediate housing 11, whereby the axial position of the fixed scroll 31 is determined. Further, in this state, the side surface 3111 of the 1 st substrate 311 is fixed to the 1 st inner wall surface 111 of the intermediate case 11 by press-fitting, whereby the center position is determined. By the above operation, the fixed scroll 31 can be held to the intermediate housing 11 in a state where the center position, the axial height position, and the phase with respect to the intermediate housing 11 are determined. The fixed scroll 31 is provided with a function of separating high pressure from low pressure in the casing 1. Therefore, the entire circumference of the side surface 3111 of the 1 st base plate 311 of the fixed scroll 31 and the 1 st inner wall surface 111 of the intermediate housing 11 needs to be pressurized by the press fit so that the refrigerant does not leak. Therefore, the heat press-fit position is set to the 1 st inner wall surface 111 where the groove 118 is not formed.

Next, a method of adjusting the clearances (tip clearances) between the tip ends of the scrolls of the fixed scroll 31 and the orbiting scroll 32 and the respective base plates will be described with reference to fig. 15. Fig. 15 is a cross-sectional view showing the K portion in fig. 2 as in fig. 10, and is a diagram showing the dimensions of the respective components. When the dimensions of the respective portions are set as described below, the tip clearance Q can be expressed by the following equation.

L＝M+Q+N+T+P

I.e. q=l-M-N-T-P.

Here, when the dimensions of the respective portions are known by measurement, the target tip clearance Q can be obtained by adjusting the thickness T of the thrust plate 24 that can be produced in a large amount at most. The target tip clearance Q is herein defined as 71±5 μm. Here, the value is a numerical value of a representative model, and the target value varies according to models.

By such adjustment, the refrigerant can be prevented from leaking into the adjacent compression space through the gap between the tip of the scroll and each base plate, and the loss of the scroll compressor can be reduced.

Next, regarding the fixation of the intermediate case 11 and the main frame 2, a mechanism of deformation of the main frame 2 at the time of fixation will be described with reference to fig. 16 to 19. Fig. 16 to 19 are enlarged cross-sectional views showing the main frame 2 and the portion of the orbiting scroll 32. The Z axis 28 shown in fig. 16 to 19 is a straight line perpendicular to the flat surface 212 of the main frame 2 and passing through the center of the outer diameter portion where the stress F is generated. In fig. 16, a swing scroll 32 is mounted on the main frame 2. As shown in fig. 16, in this state, stress F generated by the press-fit of the intermediate housing 11 is generated in the surface of the outer diameter portion of the main frame 2, and the flat surface 212 of the main frame 2 is deformed as shown in fig. 17. In fig. 17, the deformation of the main frame 2 in the case where the suction port 213 is located on one side of the Z axis 28 is shown, and the suction port 213 is a portion having low rigidity against bending moment caused by stress F generated by compressive load applied in the radial direction. As the portion 25 having lower rigidity than other components in the main frame 2, there are a pin hole for positioning required at the time of machining, a hole for suppressing vibration rotation at the time of vibration, an euclidean groove, a hole for determining the phase of the fixed scroll, and the like, in addition to the suction port 213.

In fig. 18 and 19, the deformation of the main frame 2 in the case where the portions 25 having low rigidity are located on both sides of the Z axis 28 is shown. As shown in fig. 19, the flatness of the flat surface 212 when the main frame 2 is deformed is better when the portions 25 with lower rigidity are located on both sides of the Z axis 28 than when the main frame 2 is deformed when the portions 25 with lower rigidity are located on one side of the Z axis 28 as shown in fig. 17. Therefore, when the flat surface 212 of the main frame 2 is used as a reference surface, the inclination of the orbiting scroll 32 with respect to the flat surface 212 is small when the orbiting scroll 32 is disposed above the main frame 2. This makes it possible to assemble the tip clearance Q with high accuracy, thereby suppressing leakage into the adjacent compression space and reducing loss of the scroll compressor.

Further, since the deterioration of the flatness of the flat surface 212 of the main frame 2 can be suppressed, the increase of the sliding resistance of the orbiting scroll 32 can be suppressed, and the deterioration of the performance of the scroll compressor can be suppressed.

Next, the arrangement of the portions 25 of the main frame 2 having low rigidity in the structure of the main frame 2 will be described with reference to fig. 20 and 21. Fig. 20 is a top view showing the main frame, and fig. 21 is a sectional view taken along a plane passing through the X-axis 26 in fig. 20. The Z axis 28 is a straight line perpendicular to the flat surface 212 of the main frame 2 and passing through the center of the outer peripheral surface of the main frame 2. The Y axis 27 is a straight line passing through the center of the 1 st euclidean groove 215 and intersecting the Z axis 28. Further, the X axis 26 is a straight line perpendicular to the Y axis 27, and is a straight line intersecting the Z axis 28.

In the case where the 1 st part 251 having low rigidity of the main frame 2 is provided across the 2 nd and 3 rd quadrants, the 2 nd part 252 having low rigidity is provided across the 1 st and 4 th quadrants. In fig. 20, a pair of

portions

251, 252 having low rigidity are located at symmetrical positions with respect to the Y axis 27, and are opposed to each other across the Z axis 28, which is the central axis of the main frame 2. That is, 2 portions 1

st

251 and 2 nd 252 having low rigidity, which are portions having low rigidity, are provided on both left and right sides with respect to a Y axis (1 st axis) which is a straight line passing through the center of the 1 st euclidean groove 215 and intersecting the Z axis 28, and when a straight line perpendicular to the Y axis 27 and intersecting the Z axis 28, which is a straight line passing through the center of the outer peripheral surface of the main frame 2, is set as the X axis 26 (2 nd axis), the portions 1

st

251 and 2 nd 252 having low rigidity are arranged so as to cross the X axis 26.

In fig. 20,

portions

251 and 252 of the main frame 2 having low rigidity are shown as identical shapes. However, there is no problem about the asymmetry, different shape, and different number of the X-axis 26 and the Y-axis 27.

For example, as shown in fig. 22, a hole 220 may be provided. The shape of the portion 25 may be asymmetric about the X-axis 26 or the Y-axis 27 than the shape of the portion 25 having lower rigidity. Further, it may be set in a different shape or in a different number.

The shape of the portion 25 having low rigidity may be a hole, a slit, a groove, or the suction port 213. Fig. 23 is a plan view showing a case where the slit 230 is provided. Fig. 24 is a plan view showing a case where the hole 240 is provided. Fig. 25 is a plan view showing a case where the groove 250 is provided. These are provided to suppress deterioration of the flatness of the flat surface 212 of the main frame 2.

In the case where the portion 25 having low rigidity is the suction port 213, it is preferable that a part of the suction port 213 is located outside the locus of the orbiting scroll 32 during the orbiting motion so as to allow the refrigerant to pass through the main frame 2. This is to prevent the 2 nd base plate 321 of the orbiting scroll 32 from blocking the refrigerant passage. That is, when the suction port 213 corresponds to a portion having low rigidity, the portion 25 having low rigidity is located on the outer diameter side of the orbiting scroll 32.

Embodiment 2

Embodiment 2 will be described below with reference to the drawings. Fig. 26 is a top view showing the main frame, and fig. 27 is a sectional view taken along a plane passing through the X-axis in fig. 26. In the present embodiment, regarding the structure of the main frame 2, the portion 100 having high rigidity of the main frame 2 is arranged. The Z axis 28 is a straight line perpendicular to the flat surface 212 of the main frame 2 and passing through the center of the outer diameter. The Y axis 27 is a straight line passing through the center of the 1 st euclidean groove 215 and intersecting the Z axis 28. Further, the X axis 26 is a straight line perpendicular to the Y axis 27, and is a straight line intersecting the Z axis 28.

When the portion 25 of the main frame 2 having low rigidity is provided across the 2 nd and 3 rd quadrants as shown in fig. 26, the portion 100 having high rigidity is provided across the 2 nd and 3 rd quadrants as shown in fig. 27. As shown in fig. 27, a portion 100 having a thickness provided circumferentially across the 2 nd and 3 rd quadrants is a portion having high rigidity, and this portion is a rib. That is, the portions 100 having high rigidity are provided at positions corresponding to the circumferential positions of the portions 25 having low rigidity of the main frame 2. Here, in fig. 26, the position corresponding to the circumferential position refers to an angular range θ in which the portion 25 having low rigidity is provided, and the portion 100 having high rigidity is provided in the same angular range θ as that.

As shown in fig. 16, the moment of inertia of the cross section with respect to the bending moment caused by the stress F generated by the compressive load applied in the radial direction is larger than the moment of inertia of the cross section in the 1 st and 4 th quadrants, and therefore the rigidity in the 2 nd and 3 rd quadrants is higher than the rigidity in the 1 st and 4 th quadrants. The

portions

25 and 100 having low rigidity and high rigidity are located in the same phase (the same position corresponding to the circumferential position). In this case, the same phase is merely referred to, and there is a degree of freedom in the radial direction. In addition, as in the structure shown in fig. 22, the portions 100 having higher rigidity may be asymmetric portions with respect to the X-axis 26 and the Y-axis 27, portions having different shapes, or portions having different numbers.

In addition, although the above description has been given of the case where the rib is provided integrally with the main frame 2 as a portion of the main frame 2 having high rigidity, as shown in fig. 28, a member different from the main frame 2 may be provided instead of the rib. In fig. 28, a case of mounting a bracket 281 as a different component with a screw 280 is shown. In this way, even if a portion having high rigidity is disposed at a position where compensation rigidity is low, deterioration in flatness of the flat surface 212 of the main frame 2 can be suppressed as in embodiment 1. In addition, if the portions 25 having low rigidity exist symmetrically left and right, the portions having high rigidity are not required.

Embodiment 3

Embodiment 3 will be described below with reference to the drawings. Fig. 29 is a perspective view of the main frame from one end side (see fig. 2), fig. 30 is a perspective view of the main frame from the other end side, and fig. 31 and 32 are plan views of the main frame from the other end side. In the figure, the main frame 2 is provided with

ribs

100A, 100B, 100C, 100D, 100E, 100F as portions having high rigidity. In the present embodiment, as shown by a broken line (see fig. 30 and 31), the

truss structures

29A, 29B, and 29C are configured by the

ribs

100A, 100B, 100C, 100D, 100E, and 100F, the main body portion 21, and the main bearing portion 22, which are portions of the main frame 2 having high rigidity, with respect to the structure of the main frame 2. For example, the truss structure 29A is composed of the rib 100A, the main bearing portion 22, the rib 100F, and the main body portion 21, the rib 100F is rigidly joined to the main body portion 21 via the joint 29A1, the rib 100A is rigidly joined to the main body portion 21 via the joint 29A2, and the rib 100F is rigidly joined to the main bearing portion 22 and the rib 100A is rigidly joined to the main bearing portion 22 via the joint 29A 3. The

truss structures

29B and 29C are also configured in the same manner. In this configuration, the joints 29A1, 29A2 … … C3 are rigidly joined to form

truss structures

29A, 29B, 29C.

As shown in fig. 30 and 31,

ribs

100A, 100B, 100C, 100D, 100E, and 100F are provided as portions having high rigidity from the main body portion 21 of the main frame 2 toward the main bearing portion 22. That is, one axial end side of the

ribs

100A, 100B, 100C, 100D, 100E, 100F on the body portion 21 side of the

ribs

100A, 100B, 100C, 100D, 100E, 100F, which are connection portions of the

ribs

100A, 100B, 100C, 100D, 100E, 100F with the body portion 21 of the main frame 2, is connected to a portion of the main frame 2 that contacts the housing 1. Here, the axial direction refers to a vertical direction in which the compressor is mounted as shown in fig. 2. Further, the circumferential position of the axial one end side of the main body portion 21 side of the

ribs

100A, 100B, 100C, 100D, 100E, 100F is located within the circumferential range of the main body portion 21 to which stress is applied (in fig. 31, for example, regarding the

ribs

100A, 100B, the axial one end side of the main body portion 21 side is located within the circumferential range 200). As shown in fig. 31, the circumferential positions of the

ribs

100A, 100B, 100C, 100D, 100E, 100F on the other end side in the axial direction of the main bearing portion 22 side of the main frame 2 are located within the circumferential range of the

portions

25A, 25B, 25C having low rigidity (for example, the circumferential positions of the other end side in the axial direction of the main bearing portion 22 side of the rib 100A are located within the circumferential range 300 of the portion 25A having low rigidity) as the connection portions of the

ribs

100A, 100B, 100C, 100D, 100E, 100F and the main bearing portion 22 of the main frame 2.

Accordingly, when the main frame 2 is fixed to the housing 1 by the press-fitting or the like, deformation of the main frame 2 due to stress generated at the contact portion between the main frame 2 and the housing 1 can be suppressed. That is, since the

truss structures

29A, 29B, 29C are employed as described above, even if internal stress is generated in the main frame 2, deterioration in flatness of the flat surface 212 of the main frame 2 can be prevented. Further, the

ribs

100A and 100B are disposed bilaterally symmetrically about the center Q of the surface of the main body portion 21 that contacts the housing 1. The same applies to the

ribs

100C and 100D and the

ribs

100E and 100F. Accordingly, when the main frame 2 is fixed to the housing 1 by the press-fitting or the like, the deformation of the main frame 2 due to the stress generated at the contact portion of the main frame 2 and the housing 1 is symmetrical, and therefore, the deterioration of the flatness of the flat surface 212 of the main frame 2 can be suppressed.

In this case, as shown by the broken line, the truss structure 29A is composed of the main body portion 21, the

portions

100A and 100F having high rigidity, and the main bearing portion 22. The truss structure 29B is composed of the main body portion 21, the

portions

100B and 100C having high rigidity, and the main bearing portion 22, as shown by broken lines, similarly to the truss structure 29A. The truss structure 29C is composed of the main body portion 21, the

portions

100D and 100E having high rigidity, and the main bearing portion 22, as shown by broken lines, similarly to the

truss structures

29A and 29B. As shown in fig. 31 and 32, in the truss structure 29A, adjacent ribs 100A are connected to the other end side of the main bearing portion 22 side of the rib 100F in the axial direction. In the truss structure 29B, the adjacent rib 100B is connected to the other end side of the main bearing portion 22 side of the rib 100C in the axial direction. In the truss structure 29C, the adjacent rib 100D is connected to the other end side of the main bearing portion 22 side of the rib 100E in the axial direction.

Accordingly, when the main frame 2 is fixed to the housing 1 by the press-fitting or the like, deformation of the main frame 2 due to stress generated at the contact portion between the main frame 2 and the housing 1 can be suppressed. The

truss structures

29A, 29B, 29C shown in fig. 30 and 31 are as follows: when stress is generated in the main body 21 of the main frame 2, bending moment generated by internal stress generated in the main body 21, the

portions

100A, 100B, 100C, 100D, 100E, 100F, and the main bearing 22 having high rigidity can be suppressed. Therefore, deterioration in flatness of the flat surface 212 of the main frame 2 can be suppressed. As shown in fig. 32,

adjacent ribs

100A and 100F are provided so as to partially contact with each other at a broken line portion R of the main bearing portion 22. The same applies to the relationship between the

ribs

100B and 100C, and also the relationship between the

ribs

100D and 100E.

Embodiment 4

Embodiment 4 will be described below with reference to the drawings. Fig. 33 is a perspective view of the main frame from one end side, fig. 34 is a perspective view of the main frame from the other end side, and fig. 35 and 36 are plan views of the main frame from the other end side. In the figure,

portions

100A, 100B, 100C, 100D, 100E, 100F, 100G, and 100H having high rigidity are provided in the main frame 2. In the present embodiment, as shown by a broken line (see fig. 34 and 35), the

truss structures

29A, 29B, 29C, and 29D are formed by the

ribs

100A, 100B, 100C, 100D, 100E, 100F, 100G, and 100H, the main body 21, and the main bearing 22, which are portions of the main frame 2 having high rigidity, with respect to the structure of the main frame 2. For example, the truss structure 29A is composed of the rib 100A, the main bearing portion 22, the rib 100H, and the main body portion 21, the rib 100H is rigidly joined to the main body portion 21 via the joint 29A1, the rib 100A is rigidly joined to the main body portion 21 via the joint 29A2, and the rib 100H is rigidly joined to the main bearing portion 22 and the rib 100A is rigidly joined to the main bearing portion 22 via the joint 29A 3. The

truss structures

29B, 29C, and 29D are also configured in the same manner. In this configuration, the joints 29A1, 29A2 … … D3 are rigidly joined to form

truss structures

29A, 29B, 29C, 29D.

As shown in fig. 34 and 35,

portions

100A, 100B, 100C, 100D, 100E, 100F, 100G, and 100H, which are portions having high rigidity, are provided from the main body portion 21 of the main frame 2 toward the main bearing portion 22. That is, one axial end side of the

ribs

100A, 100B, 100C, 100D, 100E, 100G, 100H, which are connecting portions of the

ribs

100A, 100B, 100C, 100D, 100E, 100F, 100G, 100H with the main body 21 of the main frame 2, is connected to a portion of the main frame 2 that contacts the housing 1. Here, the axial direction refers to a vertical direction in which the compressor is mounted as shown in fig. 2. In addition, as in the case of embodiment 3, the circumferential position of the axial one end side of the main body portion 21 side of the

ribs

100A, 100B, 100C, 100D, 100E, 100F, 100G, 100H is located within the circumferential range of the main body portion 21 to which the stress is applied.

As shown in fig. 35, circumferential positions of the other end sides in the axial direction of the

ribs

100A, 100B, 100C, 100D, 100E, 100F, 100G, 100H, which are connecting portions between the main bearing portion 22 side of the

ribs

100A, 100B, 100C, 100D, 100E, 100F, 100G, 100H and the main bearing portion 22 of the main frame 2, are located within the circumferential ranges of the

portions

25A, 25B, 25C, 25D having low rigidity. Accordingly, when the main frame 2 is fixed to the housing 1 by the press-fitting or the like, deformation of the main frame 2 due to stress generated at the contact portion between the main frame 2 and the housing 1 can be suppressed. That is, since the

truss structures

29A, 29B, 29C, 29D are employed as described above, even if internal stress is generated in the main frame 2, deterioration in the flatness of the flat surface 212 of the main frame 2 can be prevented.

Further, the

ribs

100A and 100B are disposed bilaterally symmetrically about the center of the face of the main body portion 21 that contacts the housing 1. The same applies to the

ribs

100C and 100D, the

ribs

100E and 100F, and the

ribs

100G and 100H. Accordingly, when the main frame 2 is fixed to the housing 1 by the press-fitting or the like, the deformation of the main frame 2 due to the stress generated at the contact portion of the main frame 2 and the housing 1 is symmetrical, and therefore, the deterioration of the flatness of the flat surface 212 of the main frame 2 can be suppressed. In this case, as shown by the broken line, the truss structure 29A is composed of the main body portion 21, the

portions

100A and 100H having high rigidity, and the main bearing portion 22. The truss structure 29B is composed of the main body portion 21, the

portions

truss structures

29A and 29B. The truss structure 29D is also composed of the main body portion 21, the

portions

100F and 100G having high rigidity, and the main bearing portion 22, as indicated by broken lines, similarly to the

truss structures

29A, 29B, and 29C.

As shown in fig. 35 and 36, in the truss structure 29A, adjacent ribs 100A are connected to the other end side of the main bearing portion 22 side of the rib 100H in the axial direction. In the truss structure 29B, the adjacent rib 100B is connected to the other end side of the main bearing portion 22 side of the rib 100C in the axial direction. In the truss structure 29C, the adjacent rib 100D is connected to the other end side of the main bearing portion 22 side of the rib 100E in the axial direction. In the truss structure 29D, the adjacent rib 100F is connected to the other end side of the main bearing portion 22 side of the rib 100G in the axial direction. Accordingly, when the main frame 2 is fixed to the housing 1 by the press-fitting or the like, deformation of the main frame 2 due to stress generated at the contact portion between the main frame 2 and the housing 1 can be suppressed. The

truss structures

29A, 29B, 29C, 29D shown in fig. 34 and 35 are as follows: when stress is generated in the main body portion 21 of the main frame 2, bending moment generated by internal stress generated in the main body portion 21, the

portions

100A, 100B, 100C, 100D, 100E, 100F, 100G, 100H, and the main bearing portion 22 having high rigidity can be suppressed. Therefore, deterioration in flatness of the flat surface 212 of the main frame 2 can be suppressed. As shown in fig. 36,

adjacent ribs

100A and 100H are provided so as to partially contact with each other at a broken line portion R of the main bearing portion 22. The same applies to the relationship between the

ribs

100B and 100C, the relationship between the

ribs

100D and 100E, and the relationship between the

ribs

100F and 100G.

While various illustrative embodiments and examples have been described herein, the various features, aspects, and functions described in one or more embodiments are not limited to the application of the particular embodiments, and may be applied to the embodiments alone or in various combinations.

Accordingly, numerous modifications not illustrated can be envisaged within the scope of the technology disclosed in the present application. For example, the case where at least 1 component is deformed, added or omitted, or the case where at least 1 component is extracted and combined with the components of other embodiments is included.

Description of the reference numerals

1: a housing; 2: a main frame; 21: a main body portion; 22: a main bearing portion; 215: a 1 st Euclidean groove; 25. 25A, 25B, 25C, 25D: a portion having low rigidity; 251: part 1; 252: part 2; 31: a fixed scroll; 312: a 1 st scroll; 32: a swinging scroll; 322: a 2 nd scroll; 324: 2 nd Euclidean groove; 33: an euler ring; 332: a 1 st key portion; 333: a 2 nd key portion; 34: a compression chamber; 100. 100A, 100B, 100C, 100D, 100E, 100F, 100G, 100H: a portion with higher rigidity.

Claims

1. A scroll compressor is provided with: a fixed scroll having a 1 st scroll body; a orbiting scroll having a 2 nd scroll body, the 2 nd scroll body and the 1 st scroll body being engaged with each other to form a compression chamber; an Oldham ring provided with a 2 nd key portion, the 2 nd key portion being received in a pair of 2 nd Euclidean grooves provided in the orbiting scroll; a main frame provided with a pair of 1 st Euclidean grooves for receiving a pair of 1 st keys provided on the Euclidean ring; and a housing that accommodates the fixed scroll, the orbiting scroll, and the main frame on an inner side,

2. The scroll compressor of claim 1, wherein,

the 1 st and 2 nd portions are arranged bilaterally symmetrically about the 1 st axis.

3. A scroll compressor is provided with: a fixed scroll having a 1 st scroll body; a orbiting scroll having a 2 nd scroll body, the 2 nd scroll body and the 1 st scroll body being engaged with each other to form a compression chamber; an Oldham ring provided with a 2 nd key portion, the 2 nd key portion being received in a pair of 2 nd Euclidean grooves provided in the orbiting scroll; a main frame provided with a pair of 1 st Euclidean grooves for receiving a pair of 1 st keys provided on the Euclidean ring; and a housing that accommodates the fixed scroll, the orbiting scroll, and the main frame on an inner side,

4. The scroll compressor of claim 3, wherein,

the portions of higher rigidity are ribs.

5. The scroll compressor of claim 4, wherein,

an axial one end side of the rib on the main body side, which is a connection portion of the rib to the main body of the main frame, is connected to a portion of the main frame that contacts the housing.

6. The scroll compressor of claim 4 or 5, wherein,

the circumferential position of the other end side in the axial direction of the main bearing portion side of the rib, which is a connection portion of the rib with the main bearing portion of the main frame, is located within a circumferential range of a portion having low rigidity.

7. The scroll compressor of claim 6, wherein,

among the adjacent 2 ribs, the other end side in the axial direction of the main bearing portion side is continuous.

8. The scroll compressor of any one of claims 5 to 7, wherein,

the plurality of ribs are provided, and 2 of the plurality of ribs are provided bilaterally symmetrically about a center of a face of the main frame that contacts the housing.

9. The scroll compressor of claim 3, wherein,

the portion having higher rigidity is a member different from the main frame.

10. The scroll compressor of any one of claims 1 to 9, wherein,

the less rigid portions are holes, slots or cutouts.

11. The scroll compressor of any one of claims 1 to 10, wherein,

the portion having low rigidity is located on the outer diameter side of the orbiting scroll.