JP2020020291A - Compressor - Google Patents

Abstract

To provide a compressor capable of reducing the total number of fastening bolts for fastening components of a compression mechanism part and the compression mechanism part and a housing, and of avoiding the worsened assemblability of components of the compressor.SOLUTION: A compression mechanism part 30 includes a fixed scroll member 32, a turning scroll member 34, and a bearing member 36 forming a bearing part 361a to rotatably support a driving shaft 14 and fixed to the fixed scroll member 32 with a plurality of fastening bolts 70. A plurality of first bolts 71 out of the plurality of fastening bolts 70 fasten only two components, namely, the fixed scroll member 32 and the bearing member 36, out of three components, namely, the fixed scroll member 32, the bearing member 36, and a housing 12. A plurality of second bolts 72 out of the plurality of fastening bolts 70 fasten the three components to one another.SELECTED DRAWING: Figure 2

Description

The present invention relates to a scroll type compressor that compresses and discharges drawn refrigerant. In particular, the present invention is used in a refrigeration cycle device using a CO ₂ refrigerant having a large difference in high and low pressures, and is effective in a compressor requiring a high level of durability because a high load acts on a bearing portion. Further, the present invention is effective in a compressor having a high need for reduction in size and weight, such as a vehicle-mounted compressor.

  Patent Document 1 discloses a scroll-type compressor. The compressor includes a scroll-type compression mechanism, a drive shaft for driving the compression mechanism, and a plurality of bolts for fastening components of the compression mechanism. The compression mechanism has a fixed scroll member and an orbiting scroll member. The drive shaft has a fixed crank mechanism for turning the orbiting scroll member.

  In assembling the components of the compressor, first, the centering assembly of the compression mechanism is performed. In the centering assembly of the compression mechanism, the components of the compression mechanism are temporarily fastened and fixed to each other by a plurality of bolts. In this state, the fixed scroll member and the orbiting scroll member are aligned. Thereafter, the components of the compression mechanism are fastened and fixed by a plurality of bolts. After the centering of the compression mechanism, the compression mechanism is inserted into the housing. Thereafter, the compression mechanism and the housing are fixed by welding or press fitting.

Japanese Patent No. 6225626

  The inventor of the present invention has described a plurality of compression mechanism bolts that fasten the components of the compression mechanism and do not fasten the compression mechanism and the housing to each other. The use of two types of bolts, i.e., a plurality of housing bolts for fastening the compression mechanism and the housing, was studied without fastening the compression mechanism.

  However, in this case, the total number of bolts is increased and the number of parts is increased as compared with the case where only the compression mechanism bolt is used among the compression mechanism bolt and the housing bolt. For this reason, the manufacturing cost of the compressor increases.

  Further, in this case, it is necessary to increase the space for arranging the bolts as compared with the case where only the bolts for the compression mechanism are used. If the space in which the bolts are arranged is increased while maintaining the overall size of the compressor, the suction passage is reduced, and the installation space for the anti-rotation mechanism is reduced. When the installation space for the rotation preventing mechanism is reduced, the rigidity of the rotation preventing mechanism is reduced. Further, if the space for installing the bolts is increased while maintaining the space for installing the suction passage and the rotation preventing mechanism, the physical size of the entire compressor is increased. It is conceivable that the total number of bolts may be reduced by increasing the shaft diameter of the bolts to increase the bolt axial force. However, even in this case, as the shaft diameter of the bolt is increased, the space for arranging the bolt is increased, and the physical size of the entire compressor is increased.

  Therefore, as a method of avoiding an increase in the total number of bolts, the present inventor considers all bolts for the compression mechanism to be co-tightening bolts for co-fastening a plurality of components of the compression mechanism and the housing. did. The co-fastening bolt serves both as a bolt for fastening the components of the compression mechanism and the bolt for fastening the compression mechanism to the housing.

  However, if all of the bolts for the compression mechanism are co-tightened bolts, the centering of the compression mechanism cannot be performed before the compression mechanism is housed in the housing. That is, the assemblability of the components of the compressor deteriorates.

  In view of the above, the present invention can reduce the total number of fastening bolts for fastening the components of the compression mechanism unit and fastening the compression mechanism unit and the housing, and can reduce the number of components of the compressor. It is an object of the present invention to provide a compressor capable of avoiding deterioration of the assemblability of the compressor.

To achieve the above object, according to the first aspect of the present invention,
The compressor that compresses and discharges the sucked refrigerant,
A scroll-type compression mechanism (30);
A drive shaft (14) for transmitting a driving force to the compression mechanism,
A housing (12) for housing the compression mechanism and the drive shaft;
A plurality of fastening bolts (70) for fastening the components of the compression mechanism,
The compression mechanism is
A fixed scroll member (32) fixed to the housing;
A orbiting scroll member (34) that is arranged alongside the fixed scroll member in the axial direction of the drive shaft and engages with the fixed scroll member to compress the refrigerant when orbiting by the driving force of the drive shaft;
A bearing member (361a) for rotatably supporting the drive shaft, and a bearing member (36) fixed to the fixed scroll member by a plurality of fastening bolts;
The plurality of fastening bolts include a plurality of first bolts (71) and a plurality of second bolts (72, 73),
The plurality of first bolts fasten only two parts of the fixed scroll member, the bearing member, and the bearing member among the three parts of the fixed scroll member, the bearing member, and the housing,
The plurality of second bolts fasten the three parts together.

  According to this, two parts, the fixed scroll member and the bearing member, are fastened by the plurality of first bolts. The three components of the fixed scroll member, the bearing member, and the housing are fastened together by a plurality of second bolts.

  For this reason, in assembling the components of the compressor, the centering of the compression mechanism can be performed using the plurality of first bolts before the compression mechanism is inserted into the housing. After inserting the compression mechanism unit with the centering assembly into the housing, the fixed scroll member and the bearing member can be fixed using the plurality of second bolts, and at the same time, the compression mechanism unit can be fixed to the housing. Therefore, it is possible to avoid deterioration of the assemblability of the components of the compressor when all of the plurality of fastening bolts are bolts for co-fastening.

  Further, according to this, the plurality of second bolts also serve as bolts for fastening the fixed scroll member and the bearing member and bolts for fastening the compression mechanism and the housing. For this reason, compared with the case of using two types of bolts, a compression mechanism bolt for fastening the fixed scroll member and the bearing member, and a housing bolt for fastening the compression mechanism portion and the housing, the total number of bolts is reduced. Can be reduced.

  As a result, the number of parts can be reduced. Therefore, the manufacturing cost of the compressor can be reduced as compared with the case where two types of bolts are used. Furthermore, by reducing the total number of bolts, it is possible to avoid a reduction in the suction passage that occurs when two types of bolts are used. Further, it is possible to avoid a decrease in rigidity of the rotation preventing mechanism due to a reduction in the installation space of the rotation preventing mechanism. Furthermore, by reducing the total number of bolts, it is possible to suppress an increase in the space in which the bolts are arranged. For this reason, an increase in the physique of the entire compressor can be suppressed. Thereby, in the downsized compressor, the downsizing of the compressor can be maintained, and the product competitiveness can be maintained.

  A comparison between the bolt axial force required for fixing the components of the compression mechanism and the bolt axial force required for fixing the compression mechanism to the housing shows that the bolt axial force required for fixing the compression mechanism is It is generally larger. For this reason, even if a part of the plurality of bolts for fastening and fixing the fixed scroll member and the bearing member of the compression mechanism portion are used for fixing the compression mechanism portion and the housing, it is necessary to fix the compression mechanism portion and the housing. A high axial force can be obtained.

  In addition, the reference numerals in parentheses attached to the respective components and the like indicate an example of a correspondence relationship between the components and the like and specific components and the like described in the embodiments described later.

It is a figure showing composition of a refrigeration cycle device in a 1st embodiment. It is a sectional view of a compressor in a 1st embodiment. FIG. 3 is a front view of one end surface of the fixed scroll member in FIG. 2. It is sectional drawing of the compressor in 1st Embodiment, and is a figure which shows the working load which acts between a compression mechanism part and a housing. It is a figure showing arrangement of the 2nd bolt. It is sectional drawing of the compressor in 1st Embodiment, and is a figure which shows the working load which acts between a compression mechanism part and a housing. It is a figure showing arrangement of a plurality of 2nd bolts. It is a figure showing arrangement of a plurality of 2nd bolts, and acting load. It is a graph which shows the change of (alpha) value in Formula (3) with respect to the arrangement | positioning angle of 2nd bolt when the number of 2nd bolts is three. FIG. 7B is a diagram showing an arrangement of three second bolts when the α value is maximum in FIG. 7A. FIG. 7B is a diagram showing an arrangement of three second bolts when the α value is maximum in FIG. 7A. It is a graph which shows the change of (alpha) value in Formula (3) with respect to the arrangement | positioning angle of a 2nd bolt when the number of 2nd bolts is five. It is a figure which shows arrangement | positioning of five 2nd bolts when (alpha) value becomes the maximum in FIG. 8A. It is a figure which shows arrangement | positioning of five 2nd bolts when (alpha) value becomes the maximum in FIG. 8A. It is a graph which shows the change of (alpha) value in Formula (3) with respect to the arrangement | positioning angle of 2nd bolt when the number of 2nd bolts is four. FIG. 9B is a diagram showing an arrangement of four second bolts when the α value is maximum in FIG. 9A. FIG. 9B is a diagram showing an arrangement of four second bolts when the α value is maximum in FIG. 9A. It is a graph which shows the change of (alpha) value in Formula (3) with respect to the arrangement | positioning angle of 2nd bolt when the number of 2nd bolts is six. FIG. 10B is a diagram showing an arrangement of six second bolts when the α value is maximum in FIG. 10A. FIG. 10B is a diagram showing an arrangement of six second bolts when the α value is maximum in FIG. 10A. It is sectional drawing of the compressor in 3rd Embodiment. It is sectional drawing of the compressor in 4th Embodiment.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. In the following embodiments, parts that are the same or equivalent are denoted by the same reference numerals and described.

(1st Embodiment)
The compressor of the present embodiment is a vehicle-mounted compressor. The compressor is used for a refrigeration cycle device constituting a vehicle air conditioner.

  As shown in FIG. 1, a refrigeration cycle apparatus 1 includes a compressor 10 that compresses and discharges a sucked refrigerant, a radiator 2 that radiates the refrigerant discharged from the compressor 10, and a decompression of the refrigerant that flows out of the radiator 2. The apparatus includes a decompression device 3 for performing pressure reduction, and an evaporator 4 for evaporating the refrigerant decompressed by the decompression device 3. The main component of the refrigerant used in the refrigeration cycle device 1 is carbon dioxide. Lubricating oil that lubricates each sliding portion inside the compressor 10 is mixed with the refrigerant. Part of the lubricating oil circulates in the cycle together with the refrigerant. Note that the refrigerant may be a CFC-based refrigerant.

  Hereinafter, the compressor 10 will be described in detail with reference to FIG. FIG. 2 is an axial cross-sectional view showing a cross section cut along the axis CL of the drive shaft 14 of the compressor 10. Note that the up and down arrows in FIG. 2 indicate the up and down direction DRv in a state where the compressor 10 is mounted on the refrigeration cycle apparatus 1. The arrow direction DRa in FIG. 2 indicates the axial direction DRa of the drive shaft 14.

  As shown in FIG. 2, the compressor 10 includes a housing 12, a drive shaft 14, an electric motor unit 20, an inverter 25, and a scroll-type compression mechanism unit 30. The drive shaft 14, the electric motor unit 20, and the compression mechanism unit 30 are housed inside the housing 12. The compressor 10 is an electric compressor. The drive shaft 14 rotates with the electric motor unit 20 as a power source. The compression mechanism 30 is driven with the rotation of the drive shaft 14. The compressor 10 has a horizontal structure in which the axis CL of the drive shaft 14 extends substantially in the horizontal direction, and the compression mechanism unit 30 and the electric motor unit 20 are arranged in a substantially horizontal direction. The substantially horizontal direction is a direction crossing the direction of gravity.

  The housing 12 forms an outer shell of the compressor 10. The housing 12 has a housing body 121, a first lid 122, and a second lid 123. The housing body 121, the first lid 122, and the second lid 123 are made of aluminum or an aluminum alloy. The housing body 121 has a cylindrical shape having an opening 121a on one side in the axial direction DRa of the drive shaft 14 and an opening 121b on the other side in the axial direction DRa.

  The first lid portion 122 covers the opening 121a on one side at a position on one side in the axial direction DRa with respect to the housing body 121. The first lid 122 is fastened and fixed to the housing body 121 by a lid bolt (not shown). A seal member (not shown) is interposed between one end of the housing body 121 in the axial direction DRa and the first lid 122.

  The second lid portion 123 covers the opening 121b on the other side at a position on the other side in the axial direction DRa with respect to the housing body 121. The second lid 123 is fastened and fixed to the housing body 121 by a lid bolt (not shown). A seal member (not shown) is interposed between the other end of the housing body 121 in the axial direction DRa and the second lid 123. Thus, the housing 12 is sealed.

  The motor unit 20 is configured by a three-phase AC motor driven by power supply from the inverter 25. The motor unit 20 is configured as an inner rotor motor in which a rotor 22 is arranged inside a stator 21.

  The stator 21 has a stator core 211 made of a magnetic material and a coil 212 wound around the stator core 211. When power is supplied from the inverter 25, the stator 21 generates a rotating magnetic field that rotates the rotor 22.

  The rotor 22 is a cylindrical member in which the drive shaft 14 is fixed by press fitting or the like. A permanent magnet (not shown) is disposed inside the rotor 22. Further, on the side surface of the rotor 22, balance weights 221 and 222 for canceling imbalance of eccentric rotation of the orbiting scroll member 34 and the like are attached.

  The inverter 25 is a device that supplies power to the stator 21. The inverter 25 is attached to the outside of the housing 12. Specifically, the inverter 25 is attached to the second lid 123.

  When electric power is supplied from the inverter 25 to the stator 21 to generate a rotating magnetic field around the stator 21, the motor unit 20 configured as described above causes the rotor 22 and the drive shaft 14 to rotate integrally.

  Note that the inverter 25 and the motor unit 20 are electrically connected to each other via a wiring (not shown) and a sealing terminal (not shown). For this reason, the housing 12 has a closed structure. Here, in an open-type compressor in which the drive shaft 14 is exposed to the atmosphere, a shaft seal is provided to prevent refrigerant leakage from an exposed portion of the drive shaft 14. However, due to the slow leak of the refrigerant from the shaft seal portion, the refrigerant may run into a shortage of refrigerant during the operation of the compressor 10. According to the present embodiment, the electric motor unit 20 is housed inside the housing 12 having a closed structure. For this reason, the shortage of the refrigerant during operation can be avoided.

  Further, in the compressor 10 of the present embodiment, the inverter 25 can adjust the rotation speed of the compressor 10 regardless of the rotation speed of the engine. Therefore, adjustment of the cooling capacity or the heating capacity is easy.

  The housing 12 is formed with a suction port 125 for sucking the low-pressure refrigerant that has passed through the evaporator 4. Specifically, the suction port 125 is formed on the other side of the housing main body 121 in the axial direction DRa than the electric motor 20. A suction pipe (not shown) connected to the evaporator 4 is connected to the suction port 125.

  The low-pressure refrigerant that has passed through the evaporator 4 is sucked from the suction port 125 into the housing 12 in which the electric motor unit 20 is disposed. The low-pressure refrigerant sucked into the housing 12 is sucked into the compression mechanism 30 from a suction port (not shown) of the compression mechanism 30. For this reason, the inside of the housing 12 in which the electric motor unit 20 is arranged is substantially at a suction pressure, that is, a low-pressure, low-temperature atmosphere. Thereby, the electric motor unit 20 and the inverter 25 can be cooled. Therefore, the efficiency and reliability of the electric drive unit can be improved.

  A discharge port 126 for discharging the high-pressure refrigerant compressed by the compression mechanism 30 is formed in the first lid 122 of the housing 12. The discharge port 126 is formed on one side of the housing 12 in the axial direction DRa with respect to the compression mechanism 30. That is, the discharge port 126 is formed in the first lid 122.

  The drive shaft 14 has a one-side portion 141 located on one side of the rotor 22 in the axial direction DRa. The compression mechanism unit 30 is located on one side of the electric motor unit 20 in the axial direction DRa of the drive shaft 14. The one side portion 141 is engaged with the compression mechanism 30. The drive shaft 14 transmits a driving force generated by the electric motor unit 20 to the compression mechanism unit 30. The one side portion 141 is rotatably supported by a main bearing portion 361a of a main bearing member 36 of the compression mechanism 30 described later.

  The one-side portion 141 has an eccentric shaft portion 142 eccentric from the rotation center of the drive shaft 14 at one end in the axial direction DRa. Note that eccentricity is synonymous with eccentricity. The eccentric shaft 142 constitutes a crank mechanism for orbiting movement of the orbiting scroll member 34 described later. The eccentric shaft 142 is rotatably supported by an eccentric bearing 342a of the orbiting scroll member 34 described later.

  The eccentric shaft 142 is integral with the main body of the drive shaft 14. In the present embodiment, a so-called fixed crank mechanism having a constant eccentricity is employed as the crank mechanism. In addition to the fixed crank mechanism, the crank mechanism includes a so-called driven crank mechanism in which the amount of eccentricity is variable by combining an eccentric shaft portion as a separate body. However, the driven crank mechanism has two parts compared to the fixed crank mechanism, and thus has a low rigidity with respect to inclination due to the influence of a gap or the like at the fitting portion. In particular, in the case of a combination with a sliding bearing, the relative inclination of the bearing portion becomes large, and the reliability of the bearing may be greatly deteriorated. Therefore, as described above, the present embodiment employs the fixed crank mechanism.

  Further, the one side portion 141 has a flange portion 143 that extends in the vertical direction DRv. The flange 143 is provided with a balance weight 143a for suppressing the eccentric rotation of the drive shaft 14.

  The drive shaft 14 has another side portion 144 located on the other side of the rotor 22 in the axial direction DRa. The other side portion 144 is rotatably supported by a sub-bearing portion 16 a of the sub-bearing member 16. The sub bearing 16a corresponds to a second bearing.

  The sub bearing member 16 is fixed to the housing main body 121 via the pedestal 17. The pedestal 17 is an interposed member interposed between the sub-bearing member 16 and the housing main body 121. The pedestal 17 has an annular plate portion 171 extending in the vertical direction DRv, and a cylindrical portion 172 extending from the outer peripheral portion of the plate portion 171 to one side in the axial direction DRa. The pedestal 17 is fixed with the cylindrical portion 172 in contact with the housing main body 121. The pedestal 17 has a through hole 173 through which the refrigerant introduced from the suction port 125 flows toward the electric motor unit 20.

  The sub bearing member 16 has a cylindrical bearing forming portion 161 and a connecting portion 162 that extends from an end of the bearing forming portion 161 in the vertical direction DRv. The bearing forming portion 161 forms an auxiliary bearing portion 16a on the inner peripheral side of the bearing forming portion 161. The connecting portion 162 is fastened and fixed to the plate portion 171 of the pedestal 17 by the auxiliary bearing bolt 18.

  The sub bearing member 16 and the pedestal 17 are made of a steel material or an aluminum alloy. The sub-bearing 16a is made of a material for a sliding bearing.

  The compression mechanism 30 has a fixed scroll member 32, an orbiting scroll member 34, and a main bearing member 36. The fixed scroll member 32 is fixed to the housing 12. The orbiting scroll member 34 compresses the refrigerant by engaging with the fixed scroll member 32 when orbiting by the driving force of the drive shaft 14. The orbiting scroll member 34 is arranged so as to be aligned with the fixed scroll member 32 in the axial direction DRa. The orbiting scroll member 34 is disposed on the other side of the fixed scroll member 32 in the axial direction DRa. The fixed scroll member 32 and the orbiting scroll member 34 are made of a steel material or an aluminum alloy.

  An Oldham ring (not shown) is connected to the orbiting scroll member 34. The Oldham ring constitutes a rotation preventing mechanism for preventing the rotation around the eccentric shaft 142. When the drive shaft 14 rotates, the orbiting scroll member 34 makes a revolving motion about the axis CL of the drive shaft 14 without revolving around the eccentric shaft portion 142. In other words. When the drive shaft 14 rotates, the orbiting scroll member 34 makes a orbital movement about the axis CL of the drive shaft 14.

  The orbiting scroll member 34 has an orbiting substrate portion 341 formed in a disk shape. The swivel board portion 341 has a cylindrical bearing forming portion 342 at a substantially central portion thereof. The bearing forming portion 342 has an eccentric bearing portion 342a that rotatably supports the eccentric shaft portion 142 on the inner peripheral side of the bearing forming portion 342. The eccentric bearing portion 342a is separate from the turning board portion 341 and is made of a sliding bearing material.

  The fixed scroll member 32 has a fixed substrate portion 321 formed in a disk shape. The fixed scroll member 32 has a spiral fixed tooth portion 322 that protrudes from the fixed substrate portion 321 toward the orbiting scroll member 34. On the other hand, the orbiting scroll member 34 is formed with a spiral orbiting tooth portion 343 protruding from the orbiting substrate portion 341 toward the fixed scroll member 32 side.

  The fixed tooth portion 322 and the turning tooth portion 343 mesh with each other and come into contact with each other at a plurality of locations, whereby a plurality of crescent-shaped working chambers 31 are formed. In FIG. 2, for convenience of illustration, only one of the plurality of working chambers 31 is denoted by a reference numeral.

  The working chamber 31 moves while reducing the volume from the outer peripheral side to the center side by the orbiting of the orbiting scroll member 34. Although not shown, the working chamber 31 is supplied with the refrigerant drawn into the housing 12 from the suction port 125 through a refrigerant supply passage formed in the main bearing member 36 and the like. The refrigerant in the working chamber 31 is compressed as the volume of the working chamber 31 decreases.

  A discharge hole 323 for discharging the refrigerant compressed in the working chamber 31 is formed in the center of the fixed substrate portion 321. A reed valve (not shown) serving as a check valve for preventing a backflow of the refrigerant into the working chamber 31 and a maximum opening degree of the reed valve are restricted to one end face 321 a on one side in the axial direction DRa of the fixed substrate portion 321. A stopper 324 is provided. Note that the reed valve and the stopper 324 are fastened and fixed to the fixed substrate portion 321 by fixing bolts 325.

  The main bearing member 36 is a bearing member including the main bearing portion 361a. The main bearing 361a corresponds to a first bearing. The main bearing member 36 forms a space between itself and the fixed scroll member 32. The eccentric shaft 142, the flange 143, the balance weight 143a, and the orbiting scroll member 34 are accommodated in this space.

  Specifically, the main bearing member 36 includes a bearing forming part 361, a bearing fixing part 362, and a connecting part 363. The bearing forming portion 361, the bearing fixing portion 362, and the connecting portion 363 are continuous without a seam. The bearing forming portion 361 is cylindrical. The bearing forming part 361 forms a main bearing part 361 a on the inner peripheral side of the bearing forming part 361.

  The bearing fixing portion 362 is a portion of the main bearing member 36 fixed to the fixed scroll member 32. The bearing fixing portion 362 is located radially outward of the drive shaft 14 from the orbiting scroll member 34. The bearing fixing portion 362 includes the outermost peripheral surface of the main bearing member 36 having the largest outer diameter among the main bearing members 36. One end surface 362a on one side in the axial direction DRa of the bearing fixing portion 362 contacts the fixed scroll member 32.

  The connecting portion 363 connects the bearing forming portion 361 and the bearing fixing portion 362. The bearing fixing portion 362 is located radially outward of the drive shaft 14 from the bearing forming portion 361. The connecting portion 363 extends from the bearing forming portion 361 radially outward of the drive shaft 14.

  The main bearing member 36 has a cylindrical shape whose inner and outer diameters increase stepwise from the other side to one side in the axial direction DRa. The smallest inner diameter portion of the main bearing member 36 having the smallest inner diameter forms the bearing forming portion 361. The largest outer diameter portion of the main bearing member 36 having the largest outer diameter forms a bearing fixing portion 362.

  The bearing forming portion 361, the bearing fixing portion 362, and the connecting portion 363 are made of a steel material or an aluminum alloy. The main bearing portion 361a is made of a material for a sliding bearing. In the present embodiment, the main bearing portion 361a is composed of a cylindrical steel member, a resin layer coated on the inner peripheral surface thereof, and the like. Note that the bearing forming portion 361, the bearing fixing portion 362, and the connecting portion 363 may be made of other materials. The main bearing portion 361a may be made of the same material as the bearing forming portion 361.

  Two annular thrust plates 364 and 344 are arranged between the main bearing member 36 and the orbiting scroll member 34. The thrust plate 364 on the main bearing member 36 side of the two thrust plates 364 and 344 is fixed to the main bearing member 36. The thrust plate 344 on the side of the orbiting scroll member 34 is fixed to the orbiting scroll member 34 so as to rotate integrally with the orbiting scroll member 34. For this reason, the two thrust plates 364 and 344 perform relative turning motion and slide.

  The housing main body 121 has a protrusion 60 for fixing the compression mechanism 30. The protrusion 60 is provided on the inner peripheral surface 121 c of the housing main body 121. The protrusion 60 protrudes from the housing body 121 toward the drive shaft 14. The protruding portion 60 is arranged over the entire area of the inner peripheral surface 121c in the circumferential direction. One end surface 60a on one side in the axial direction DRa of the protruding portion 60 is in direct contact with the other end surface 362b on the other side of the bearing fixing portion 362 of the main bearing member 36.

  Note that one end surface 60a of the protruding portion 60 may be in contact with the other end surface 362b via an intervening object. Therefore, in the present embodiment, the one end face 60a corresponds to a contact face that comes into contact with the end face on the other side in the axial direction of the bearing fixing portion directly or via an interposition. The protruding portion 60 corresponds to a contact surface forming portion on which a contact surface is formed.

  The compressor 10 includes a plurality of fastening bolts 70 for fastening components of the compression mechanism 30. The plurality of fastening bolts 70 fasten and fix the main bearing member 36 and the fixed scroll member 32 to form the compression mechanism 30. The plurality of fastening bolts 70 include a plurality of first bolts 71 and a plurality of second bolts 72. The plurality of second bolts 72 are longer than the plurality of first bolts 71.

  The plurality of first bolts 71 fasten only two parts of the fixed scroll member 32, the main bearing member 36, and the three parts 32, 36, 12 of the fixed scroll member 32, the main bearing member 36, and the housing 12. ing. The plurality of second bolts 72 share the above-mentioned three components 32, 36, 12 with the bearing fixing portion 362 of the main bearing member 36 sandwiched between the projecting portion 60 of the housing 12 and the fixed scroll member 32. I'm tightening. Thus, the plurality of fastening bolts 70 are configured by two types of bolts having different lengths.

  The first bolt 71 and the second bolt 72 have male screw portions 71a, 72a and head portions 71b, 72b, respectively. The male screw portions 71a and 72a are screw portions on which male screws are formed.

  The fixed scroll member 32 has a bolt insertion hole 326 into which the plurality of first bolts 71 are inserted. A plurality of female screw portions 365 corresponding to the male screw portions 71a of the plurality of first bolts 71 are formed in the bearing fixing portion 362.

  Further, the fixed scroll member 32 has a bolt insertion hole 327 into which the plurality of second bolts 72 are inserted. A bolt insertion hole 366 into which the plurality of second bolts 72 are inserted is formed in the bearing fixing portion 362. A plurality of female screw portions 61 corresponding to the male screw portions 72a of the plurality of second bolts 72 are formed on the protruding portion 60. The internal thread portions 365 and 61 are holes with internal threads formed on the inner surface.

  In the compressor 10 of the present embodiment, when the compression mechanism 30 compresses the refrigerant, the internal pressure of the working chamber 31 increases. Thus, a radial load and a thrust load act on the orbiting scroll member 34.

  This radial load acts on the eccentric shaft 142 engaged with the eccentric bearing 342a. The radial load acting on the eccentric shaft 142 is supported by the main bearing member 36 via the main bearing 361a. The radial load applied to the main bearing member 36 is supported by the plurality of fastening bolts 70.

  The radial load acting on the eccentric shaft 142 is also supported by the sub-bearing member 16 via the sub-bearing 16a. The radial load acting on the sub bearing member 16 is supported by the axial force of the sub bearing bolt 18. Further, the radial load acting on the auxiliary bearing member 16 is supported by the housing 12 via the pedestal 17.

  The thrust direction load acts on the two thrust plates 364 and 344. The thrust load acting on the two thrust plates 364 and 344 is supported by the main bearing member 36. Further, this load is supported by the plurality of fastening bolts 70.

In the compressor 10 of the present embodiment, the eccentric shaft 142, the main bearing 361a, and the sub-bearing 16a constitute a sliding bearing. Therefore, the radial load acting on the drive shaft 14 is supported by the slide bearing. By using a sliding bearing, even when a high load due to a high differential pressure acts on the bearing, such as when using a CO ₂ refrigerant, the reliability against wear deterioration is improved compared to a rolling bearing. It is possible to extend the life.

  In the scroll type compressor, the action of the driving force from the drive shaft 14 has a cantilever structure. For this reason, the compressor 10 of the present embodiment is excellent in reliability by having the auxiliary bearing portion 16a. Further, the auxiliary bearing portion 16a is more effective to support the main bearing portion 361a at a greater distance than the main bearing portion 361a. Therefore, when the sub-bearing portion 16a is arranged away from the main bearing portion 361a, the motor unit 20 is arranged between the main bearing portion 361a and the sub-bearing portion 16a, so that the space inside the housing 12 can be effectively used. Can be used.

  A high-pressure muffler chamber 51, an oil separation chamber 52, and a high-pressure oil storage chamber 53 are formed inside the first lid 122. The high-pressure muffler chamber 51 communicates with the discharge hole 323. The high-pressure muffler chamber 51 is a space for reducing the discharge pulsation of the refrigerant discharged from the discharge hole 323. The oil separation chamber 52 is in communication with the high-pressure muffler chamber 51. The oil separation chamber 52 is a space for separating lubricating oil from high-pressure refrigerant flowing from the high-pressure muffler chamber 51. The oil separation chamber 52 houses an oil separator 54 for separating lubricating oil from the high-pressure refrigerant flowing into the oil separation chamber 52. The oil separator 54 has a pipe shape. The oil separator 54 is fixed to the discharge port 126 by press fitting or the like. The high-pressure oil storage chamber 53 is a space that stores the lubricating oil separated by the oil separator 54.

  Therefore, the high-pressure refrigerant discharged from the discharge hole 323 flows into the oil separation chamber 52 via the high-pressure muffler chamber 51. When the high-pressure refrigerant flows into the oil separation chamber 52, the oil separator 54 separates the refrigerant contained in the high-pressure refrigerant from the lubricating oil. The high-pressure refrigerant separated by the oil separator 54 is discharged from the discharge port 126 toward the radiator 2 through a passage inside the oil separator 54. On the other hand, the lubricating oil separated by the oil separator 54 falls downward by its own weight and is stored in the high-pressure oil storage chamber 53.

  An oil supply passage 145 for supplying lubricating oil to each of the bearing portions 16a, 342a, 361a is formed inside the drive shaft 14. The oil supply passage 145 communicates with the high-pressure oil storage chamber 53 via an oil passage (not shown) formed in the fixed scroll member 32 and the orbiting scroll member 34. As a result, the lubricating oil stored in the high-pressure oil storage chamber 53 is supplied from the oil supply path 145 to the bearings 16a, 342a, 361a. Each bearing 16a, 342a, 361a is internally lubricated.

  Next, the assembly of the components of the compressor 10 will be described. This assembly is performed by an operator operating the machine.

  First, centering assembly of the compression mechanism 30 is performed. In this centering assembly, in a state where the drive shaft 14, the main bearing member 36, the orbiting scroll member 34, and the fixed scroll member 32 are combined, the main bearing member 36 and the fixed scroll member 32 Temporarily assembled by one bolt 71. Thereafter, the centering of the orbiting scroll member 34 and the fixed scroll member 32 is performed by centering the main bearing member 36 and the fixed scroll member 32.

  Here, the compression mechanism section 30 of the present embodiment employs a fixed crank mechanism as a crank mechanism for the orbiting movement of the orbiting scroll member 34. The fixed crank mechanism does not have a function of adjusting the turning radius of the orbiting scroll member 34, unlike a so-called driven crank mechanism. Therefore, it is necessary to determine the relative position between the fixed tooth portion 322 and the turning tooth portion 343 with high accuracy. To achieve this with the processing accuracy of individual components, extremely high-precision machining is required, which results in poor mass productivity and high cost. Therefore, in the present embodiment, in assembling the compression mechanism unit 30, a so-called centering assembling is performed, in which the bolts are fastened by aligning the units one by one.

  After the centering of the compression mechanism 30, the assembly of the compression mechanism 30 to the housing body 121 is performed. When the compression mechanism 30 is assembled to the housing body 121, the compression mechanism 30 is inserted into the housing body 121 from one side in the axial direction DRa of the housing body 121. Then, the other end surface 362b of the main bearing member 36 of the compression mechanism 30 is brought into contact with the protrusion 60 of the housing main body 121. In this state, the plurality of second bolts 72 are inserted from one side to the other side in the axial direction DRa. That is, the plurality of second bolts 72 are inserted from the side of the compression mechanism 30 where the electric motor unit 20 is not provided to the side where the electric motor unit 20 is present. The compression mechanism 30 is fastened and fixed to the housing 12 by a plurality of second bolts 72.

  According to this embodiment, a plurality of female screw portions 61 are formed on the protruding portion 60. Therefore, as described above, the plurality of second bolts 72 can be inserted from one side to the other side in the axial direction DRa. Therefore, it is easy to assemble the plurality of second bolts 72.

  After the compression mechanism 30 is assembled to the housing main body 121, the first lid 122 is fixed to the housing main body 121.

  Also, before assembling the compression mechanism 30 to the housing main body 121, the stator 21 of the electric motor 20 is assembled to the housing main body 121 in advance. At this time, the stator 21 is inserted into the housing main body 121 from the other side of the housing main body 121 in the axial direction DRa. Further, the rotor 22 of the electric motor unit 20 is fixed to the drive shaft 14 in advance by means such as shrink fitting before assembling the compression mechanism unit 30 to the housing body 121.

  Thereafter, the sub bearing member 16 and the pedestal 17 are assembled to the housing main body 121. In this assembly, the pedestal 17 is pressed into the housing main body 121. The sub bearing member 16 is fastened and fixed to the pedestal 17 by the sub bearing bolt 18. At this time, in order to minimize the relative inclination of the drive shaft 14 with respect to the bearing, the position of the sub bearing member 16 is adjusted such that the sub bearing 16a and the main bearing 361a are aligned with each other. In this state, it is fastened and fixed.

  After that, the second lid 123 is fixed to the housing main body 121. The inverter 25 is mounted on the second lid 123. Thus, the compressor 10 is assembled.

  Next, the arrangement of the plurality of fastening bolts 70 will be described with reference to FIG. FIG. 3 is a front view of one end surface 321 a of the fixed scroll member 32. In FIG. 3, the heads of the plurality of fastening bolts 70 are not shown. In FIG. 3, the plurality of second bolts 72 are hatched.

  The number of the plurality of fastening bolts 70 is eight. The breakdown includes four first bolts 71 and four second bolts 72. Therefore, the number of bolts for fastening and fixing the components of the compression mechanism 30 is eight. The number of bolts for fastening and fixing the compression mechanism 30 and the housing 12 is four.

  Here, unlike the present embodiment, there may be a case where two types of bolts, a plurality of bolts for the compression mechanism and a plurality of bolts for the housing, are arranged. The plurality of bolts for the compression mechanism are bolts that fasten components of the compression mechanism and do not fasten the housing to the compression mechanism. The plurality of housing bolts are bolts that fasten the compression mechanism and the housing without fastening the components of the compression mechanism. In this case, it is necessary to arrange a total of twelve bolts including eight compression mechanism bolts and four housing bolts.

  On the other hand, according to the present embodiment, the four bolts are also used for fastening and fixing the components of the compression mechanism 30 and for fastening and fastening the compression mechanism 30 and the housing 12. For this reason, only by arranging eight fastening bolts, the same effect as in arranging twelve bolts of two types is obtained.

  In addition, since they are also used, there is no need to newly lay out a space for arranging four housing bolts in addition to a space for arranging eight compression mechanism bolts. Thus, it is not necessary to reduce the space for the refrigerant suction path, the oil suction / discharge path, and the anti-rotation mechanism, which are not shown. Therefore, performance and reliability are not impaired.

  When two types of bolts are arranged, it is conceivable to reduce the total number of bolts by increasing the shaft diameter of the bolts and increasing the axial force per bolt. However, even in this case, an increase in the shaft diameter of the bolt increases the space for arranging the bolt. For this reason, the outer diameter of the compression mechanism increases, and the physical size of the entire compressor increases. As a result, product competitiveness decreases. On the other hand, according to the present embodiment, such a problem can be avoided.

  Further, the present inventor has studied that, different from the present embodiment, all of the plurality of fastening bolts 70 are co-fastening bolts for jointly fastening the components of the compression mechanism 30 and the housing 12. However, in this case, the centering and assembling of the compression mechanism 40 cannot be performed before the compression mechanism 30 is housed in the housing 12. That is, the assemblability of the components of the compressor 10 deteriorates.

  On the other hand, according to the present embodiment, as described above, in assembling the components of the compressor 10, before inserting the compression mechanism 30 into the housing 12, the plurality of first bolts 71 are used. The compression mechanism 30 can be centered and assembled. After inserting the compression mechanism unit 30 with the centering assembly into the housing 12, the fixed scroll member 32 and the main bearing member 36 are fixed using the plurality of second bolts 72, and at the same time, the compression mechanism unit is attached to the housing. Can be fixed. Therefore, it is possible to avoid deterioration of the assemblability of the components of the compressor 10 when all of the plurality of fastening bolts 70 are bolts for co-fastening.

Further, as shown in FIG. 3, each of the plurality of fastening bolts 70 are arranged at equal intervals centered O _P of the fixed scroll member 32 on the circumference to the center of the circle. In other words, each of the plurality of fastening bolts 70 are arranged on a circumference around the center O _P of the circle of the fixed scroll member 32. At this time, the respective centers of two bolts adjacent on the circumference of the plurality of fastening bolts 70, two straight lines forming an angle connecting the center O _P of the fixed scroll member 32 there is a uniform. Further, each of the plurality of first bolts 71 and each of the plurality of second bolts 72 are alternately arranged.

The one side end surface 321a shown in FIG. 3 corresponds to an example of a virtual plane orthogonal to the axial direction DRa at the position where the plurality of second bolts 72 are arranged in the compression mechanism 30. The center _{O P} of the fixed scroll member 32 is a position of the axis CL of the drive shaft 14. In addition, each of the plurality of fastening bolts 70 may be displaced from the circumference as long as it is disposed along the circumference. Further, "equal intervals" means that the ratio of the minimum value of each arc to the maximum value of each arc between two adjacent bolts in the circle is in the range of 0.7 to 1.0. . As described above, “equal intervals” includes not only a case where there is no difference in the length of each arc between two adjacent bolts in the circle, but also a case where there is a difference in the length of each arc. .

  In this way, the plurality of fastening bolts 70 are arranged substantially evenly along the circumference. As a result, the following effects can be obtained.

  The axial force of the plurality of fastening bolts 70, that is, the plurality of first bolts 71 and the plurality of second bolts 72 generates the fastening force of the compression mechanism 30. The plurality of fastening bolts 70 are arranged substantially uniformly along the circumference. For this reason, the fastening force of the compression mechanism 30 is generated evenly or almost uniformly at each position on the circumference where the center of the compression mechanism 30 is the center of the circle. Thereby, in a specific direction, since the axial force of the fastening bolt 70 is low, the components of the compression mechanism 30 are displaced from each other, or the compression mechanism 30 is locally deformed, and The risk that the leakage of the refrigerant increases or the like can be minimized. In addition, it is possible to prevent the balance of the axial forces of the plurality of fastening bolts 70 from being biased, causing variations in the amount of elastic deformation, and preventing the tilting of the compression mechanism 30 in the assembled state.

  The axial force of the plurality of second bolts 72 generates a fastening force between the compression mechanism 30 and the housing 12. Here, the plurality of fastening bolts 70 are arranged substantially evenly along the circumference. Each of the plurality of first bolts 71 and each of the plurality of second bolts 72 are arranged alternately. As a result, each of the plurality of second bolts 72 is also arranged substantially uniformly along the circumference. For this reason, the fastening force between the compression mechanism 30 and the housing 12 is generated evenly or almost uniformly at each position on the circumference with the center of the compression mechanism 30 as the center of the circle. As a result, the axial force of the plurality of second bolts 72 is low in a specific direction, so that the compression mechanism 30 and the housing 12 are displaced from each other or the mutual parts are locally deformed, and the housing 12 It is possible to prevent the compression mechanism 30 from relatively tilting. As a result, the drive shaft 14 and the sub-bearing portion 16a are relatively inclined, and the risk of excessive local surface pressure caused by uneven contact of the sliding bearing portion, abnormal wear caused by poor oil film formation, and risk of adhesion can be reduced. . Conversely, the above concerns can be avoided by the minimum diameter of the male screw portion 72a and the minimum number of the plurality of second bolts 72.

(2nd Embodiment)
In the present embodiment, the number of the plurality of second bolts 72 and the optimal arrangement thereof in the compressor 10 of the first embodiment will be described.

First, with respect to the applied load and moment acting between the compression mechanism 30 and the housing 12, referring to FIGS. 4A, 4B, 5A and 5B, the applied load is gravity and the applied load is a compression reaction force. Each of the two cases will be described. In the following, a second bolt 72 of the five is, on a circumference of the center O _P of the fixed scroll member 32 and the center of the circle, a case which is arranged at equal intervals as an example.

(1) As shown in gravity Figure 4A, the compressor 10 is the case of Yoko置structure, gravity _{F G} acts on the position of the center of gravity _{O G} of the compression mechanism portion 30. The gravity F _G is commensurate with the frictional force F _G between the other end surface 362b of the main bearing member 36 caused by axial force F _b of the plurality of second bolt 72, and one side end surface 60a of the protrusion 60 I have. Therefore, a moment M generated by gravity F _G, balance equations and moment M generated by the axial force F _b of the second bolt 72 is a following equation (1).

Incidentally, _{L G} in formula (1) is the distance in the axial direction DRa between the one side end face 60a and the center of gravity _{O G} of the projecting portion 60. _{F b} in the formula (1) is a axial force of the second bolt 72 in one. _Rb in the equation (1) is an arrangement radius of the second bolt 72 shown in FIG. 4B. The placement radius, the center O _P of the fixed scroll member 32 as the center of the circle, the radius of the circle passing through the centers of the plurality of second bolts 72. Θ _k in equation (1) is the arrangement angle of the second bolt 72 shown in FIG. 4B. Arrangement angles of the second bolt 72, the first reference direction is the center and the angle which the straight line forms connecting the center O _P of the compression mechanism portion 30 of the second bolt 72. The first reference direction, on one side end face 321a of the fixed scroll member 32, the center O _P of the compression mechanism portion _30, i.e., passes through the center O _P of the fixed scroll member 32 is the direction perpendicular to the direction of action of the load . Load here is a gravity F _G. Further, k in Expression (1) is an arbitrary number of the second bolt 72 that is pulled when the compression mechanism 30 is inclined. In the equation (1), n is the number of the second bolts 72 that are pulled when the compression mechanism 30 is inclined. In the example of FIG. 4B, the second bolts 72-1 and 72-2 arranged in the upper half of the fixed scroll member 32 are pulled when the compression mechanism 30 is inclined. Therefore, n is 2 in the example of FIG. 4B.

(2) Compression reaction force A radial load acts on the auxiliary bearing portion 16a as a compression reaction force. As a reaction, the drive shaft 14 receives a radial load from the auxiliary bearing portion 16a. The acting direction of the load changes with the orbital movement of the orbiting scroll member 34, that is, with the rotation of the drive shaft 14. Therefore, this load is a so-called rotational load that changes the direction of 360 ° per rotation of the drive shaft 14. However, the load value is not constant. The load value fluctuates in one rotation cycle depending on the volume change accompanying the shape of the scroll and the operating conditions. For this reason, a peak load occurs in a specific direction. In its moment, as shown in FIG. 5A, the sub-bearing portion 16a is radial peak load F _p acting as a compression reaction force. In FIG. 5A, the drive shaft 14 indicates the radial direction peak load _{F p} received from the sub-bearing portion 16a. The peak load F _p is balanced with the friction force F _p between the other end surface 362b of the main bearing member 36 caused by axial force F _b of the plurality of second bolt 72, and one side end surface 60a of the protrusion 60 ing. Therefore, a moment M generated by the radial peak load F _p acting on the sub bearing portion 16a, wherein the balance of the moment M generated by the axial force F _b of the second bolt 72, the following equation (2) Become.

Incidentally, _{L p} in formula (2) is the distance in the axial direction DRa between the other end surface 362b and the sub bearing portion 16a of the main bearing member 36. Θ _k in the equation (2) is an arrangement angle of the second bolt 72 shown in FIG. 5B. Arrangement angles of the second bolt 72, the first reference direction is the center and the angle which the straight line forms connecting the center O _P of the compression mechanism portion 30 of the second bolt 72. The first reference direction, on one side end face 321a of the fixed scroll member 32, passes through the center O _P of the compression mechanism unit 30 is a direction perpendicular to the direction of action of the load. Load here is a radial direction peak load F _p. Further, F _b , R _b , k and n in the formula (2) are the same as those in the formula (1). In the example of FIG. 5B, the second bolts 72-1, 72-2, and 72-3 arranged in the lower half of the fixed scroll member 32 are pulled when the compression mechanism 30 is inclined. Therefore, n is 3 in the example of FIG. 5B.

  The moment M in both (1) gravity and (2) compression reaction can be represented by the following general formula (3). Therefore, the general formula of the balance of the moment M by the applied load F acting between the compression mechanism 30 and the housing 12 is expressed by the following expression (3).

In addition, _Fb , _Rb , (theta) _k , k, and n in Formula (3) are the same as Formula (1). α is a constant.

The equation (3) As is clear from, the action force F of gravity F _G or radial peak load F _p, the arrangement angle theta _k of the plurality of second bolts 72, as the constant α is maximum By determining, the supporting force for the applied load F can be maximized. That is, the diameter of the male screw portion 72a of the second bolt 72 and the number of the second bolts 72 can be minimized with respect to the supporting force required in terms of specifications and operating conditions. The compressor 10 can be designed so that the overall size and manufacturing cost of the compressor 10 are minimized.

Here, the second bolt 72 that contributes to the balance of the moment M is, as shown by the hatched portion in FIG. 6, a range on the side where the tensile stress acts on the acting direction of the acting load F shown in FIG. 6, that is, 0 < The second bolt 70 is in the range of θ _k <180 °. This is because the range where the compressive stress acts does not contribute to the moment. FIG. 6 shows an example in which the acting direction of the acting load is upward. In the example of FIG. 6, there are three second bolts 72-1, 72-2, 72-3 arranged in the upper half of the fixed scroll member 32. As a premise, the bearing fixing portion 362 of the main bearing member 36 and the projecting portion 60 are elastic bodies. Further, the area on the side where the compressive stress acts between the bearing fixing portion 362 and the protruding portion 60 is in close contact. It is assumed that the range in which the tensile stress acts between the bearing fixing portion 362 and the protruding portion 60 involves minute deformation.

Next, the number of second bolts 72 and the optimal arrangement angle will be described with reference to FIGS. 7A to 10C. In the following, a second bolt 72 more are arranged at equal intervals on a circle centered on the center O _P circles of the fixed scroll member 32.

(I) When the number of second bolts 72 is two or less Although not shown, when the number of second bolts 72 is two or less, the arrangement angle of one of the second bolts 72 is θ _k = 0. When θ or θ _k = 180 °, α = 0 in Expression (3). Therefore, in equation (3), M = 0. Therefore, the second bolt 72 cannot support the moment generated by the applied load. In particular, since the compression reaction force _FP is a rotational load, the above-described state is always at least once when the drive shaft 14 makes one rotation. Therefore, it is necessary that the number of the second bolts 72 is three or more in order to stably support the compression mechanism 30.

(Ii) When the Number of Second Bolts 72 is an Odd Number of Three or More FIG. 7A shows the α value in equation (3) with respect to the arrangement angle θ of the second bolt 72 when the number of the second bolts 72 is three. 6 is a graph showing a change in the graph. 7B and 7C show the arrangement of the three second bolts 72 at the moment when the α value becomes maximum in FIG. 7A.

The arrangement angle θ in FIG. 7A is, as shown in FIGS. 7B and 7C, the center Ob1, Ob2, and Ob3 of each of the second bolts 72-1, 72-2, and 72-3 and the compression mechanism with respect to the first reference direction. of the straight line connecting the center O _P parts 30, it is the angle formed by the straight line any one. The first reference direction, on one side end face 321a of the fixed scroll member 32, passes through the center O _P of the compression mechanism 30, which is a direction orthogonal to the direction of action of the load F. In FIG. 7A, the arrangement angle θ of one specific second bolt 72 among the three second bolts 72 is shown on the horizontal axis, and the α value at that time is shown on the vertical axis.

  As is clear from FIG. 7A, the α value fluctuates in a cycle of 60 °. The arrangement angle θ when the α value becomes the peak value is 30 °, 90 °, 150 °, or the like. FIG. 7B or FIG. 7C shows the arrangement of the three second bolts 72 at the moment when the α value reaches the peak value. In FIG. 7B, the arrangement angle θ at the position of the second bolt 72-1 is 30 °, the arrangement angle θ at the position of the second bolt 72-2 is 150 °, and the position of the second bolt 72-3 is Is 270 °. In FIG. 7C, the arrangement angle θ at the position of the second bolt 72-1 is 90 °, the arrangement angle θ at the position of the second bolt 72-2 is 210 °, and the position of the second bolt 72-3 is Is 330 °.

Then, in FIG. 7B or FIG. 7C, the direction of action of the load F acting on the compression mechanism portion 30 or the drive shaft 14, as one starting from the center O _P of the compression mechanism portion 30 on the side end face 321a of the fixed scroll member 32 The direction shown on one side end surface 321a is defined as a second reference direction. Meanwhile on the side end face 321a, the line segment connecting the one of the center of the second bolt 72 marked with .smallcircle of the second bolt 72 of the three and the center O _P of the compression mechanism portion 30, a second reference direction the angle formed with respect to the support angle theta _F. The second reference direction is the reference direction for defining the support angle theta _F. At this time, support angle theta _F is 0 ° or 180 °. Thus, as α value becomes a peak value, a position supporting the angle theta _F becomes 0 ° or 180 °, it is preferable that the second bolt 72 of the three are disposed.

Further, as shown in FIG. 7A, in a range of 30 °, which is half of one cycle of 60 °, and a range centered on the angle at which the peak value is reached, the α value is equal to or more than the average value. Thus, as α value is equal to or greater than the average value, a position supporting the angle theta _F is 0 ° ± 15 ° or in the range of 180 ° ± 15 °, the second bolt 72 of the three is located Is preferred. “±” in “0 ° ± 15 °” is plus or minus.

  FIG. 8A is a graph showing a change in the α value in Expression (3) with respect to the arrangement angle θ of the second bolt 72 when the number of the second bolts 72 is five, as in FIG. 7A. 8B and 8C show the arrangement of the five second bolts 72 at the moment when the α value becomes the maximum in FIG. 8A.

The arrangement angle θ in FIG. 8A is, as shown in FIGS. 8B and 8C, the center of each of the second bolts 72-1, 72-2, 72-3, 72-4, 72-5 with respect to the first reference direction. ob1, Ob2, Ob3, Ob4, Ob5 and out of a straight line connecting the center _{O P} of the compression mechanism 30, an angle formed by the straight line any one. In FIG. 8A, the arrangement angle θ of one specific second bolt 72 among the five second bolts 72 is shown on the horizontal axis.

  As is clear from FIG. 8A, the α value fluctuates in a cycle of 36 °. The arrangement angle θ when the α value becomes the peak value is 18 °, 54 °, 90 °, or the like. The arrangement of the five second bolts 72 at the moment when the α value reaches the peak value is as shown in FIG. 8B or 8C.

Then, in FIG. 8B or FIG. 8C, the line segment connecting the one of the center of the second bolt 72 marked with .smallcircle of the second bolt 72 of five and the center O _P of the compression mechanism portion 30, the second support angle theta _F which forms with respect to a reference direction is 0 ° or 180 °. The description of the second reference direction is the same as the case where the number of the second bolts 72 is three. Thus, as α value becomes a peak value, a position supporting the angle theta _F becomes 0 ° or 180 °, it is preferable that the second bolt 72 of five are arranged.

As shown in FIG. 8A, in a range of 18 °, which is half of one cycle of 36 °, and a range centered on the angle at which the peak value is reached, the α value is equal to or larger than the average value. Thus, as α value is equal to or greater than the average value, a position supporting the angle theta _F is 0 ° ± 9 ° or within the range of 180 ° ± 9 °, the second bolt 72 of the five is located Is preferred.

In the above, the present number of the second bolt 72 is 3, the case of five, in general, if the number is an odd number of n lines, support angle theta _F is, 0 ° ± (45 / n ) ° or 180 ° ± (45 / n) °, it is preferable that n second bolts 72 are arranged. According to this, the α value in the equation (3) can be equal to or more than the average value.

(Iii) When the Number of Second Bolts 72 is an Even Number of Four or More FIG. 9A is an equation for the arrangement angle θ of the second bolts 72 when the number of the second bolts 72 is four, as in FIG. 7A. It is a graph which shows the change of (alpha) value in 3). 9B and 9C show the arrangement of the four second bolts 72 at the moment when the α value becomes maximum in FIG. 9A.

The arrangement angle θ in FIG. 9A is, as shown in FIGS. 9B and 9C, the center Ob1, Ob2, of each of the second bolts 72-1, 72-2, 72-3, 72-4 with respect to the first reference direction. ob3, Ob4 and out of a straight line connecting the center _{O P} of the compression mechanism 30, an angle formed by the straight line any one. In FIG. 9A, the arrangement angle θ of one specific second bolt 72 among the four second bolts 72 is shown on the horizontal axis, and the α value at that time is shown on the vertical axis.

  As is clear from FIG. 9A, the α value fluctuates in a cycle of 90 °. The arrangement angle θ when the α value becomes the peak value is 45 °, 135 °, 225 °, or the like. 9B and 9C show the arrangement of the four second bolts 72 at the moment when the α value reaches the peak value. 9B and 9C, the arrangement angle θ at the position of the second bolt 72-1 is 45 °. 9B and 9C, the arrangement angle θ at the position of the second bolt 72-2 is 135 °. The arrangement of the second bolt 72 in FIGS. 9B and 9C is the same.

9B and 9C, the support angle θ _L formed by the bisector Lb of the two second bolts 72 marked with “〇” among the four second bolts 72 with respect to the second reference direction is , 90 ° or 270 °. The bisector Lb is a line that bisects the angle formed by the line segment connecting the center of each of the adjacent two second bolts 72 of the plurality of second bolts 72 and the center Op of the compression mechanism 30. It is. The description of the second reference direction is the same as the case where the number of the second bolts 72 is three. 90 ° is the smaller of the angles formed by the bisector Lb with respect to the second reference direction. 270 ° is the larger of the angles formed by the bisector Lb with respect to the second reference direction. Specifically, in FIG. 9B, the support angle θ _L formed by the bisector Lb of the adjacent second bolt 72-1 and the second bolt 72-4 with respect to the second reference direction is 90 ° or 270 °. It is. Also in FIG. 9C, the bisector Lb of the second bolt 72-2 adjacent the second bolt 72-3 support angle theta _L which forms with respect to the second reference direction is 90 ° or 270 °. 4 arrangement of the second bolt 72 of the support angle theta _L is the case of 90 ° support angle theta when _L is 270 ° are the same. Thus, as α value becomes a peak value, a position supporting the angle theta _L is 90 °, it is preferable that the four second bolts 72 are arranged.

Further, as shown in FIG. 9A, in the range of 45 °, which is half of the 90 ° cycle, and the range including the peak value as the center, the α value is equal to or more than the average value. Therefore, the support angle theta _L is, the position where the range of 90 ° ± 22.5 °, it is preferable that the four second bolts 72 are arranged.

  FIG. 10A is a graph showing a change in the α value in the equation (3) with respect to the arrangement angle θ of the second bolt 72 when the number of the second bolts 72 is six, as in FIG. 7A. 10B and 10C show the arrangement of the six second bolts 72 at the moment when the α value becomes maximum in FIG. 10A.

The arrangement angle θ in FIG. 10A is, as shown in FIGS. 10B and 10C, the second bolts 72-1, 72-2, 72-3, 72-4, 72-5, 72 with respect to the first reference direction. -6 center Ob1, Ob2, Ob3, Ob4, Ob5, among straight lines connecting the centers of Ob6 and the center _{O P} of the compression mechanism 30, an angle formed by the straight line any one. In FIG. 10A, the arrangement angle θ of one specific second bolt 72 among the six second bolts 72 is shown on the horizontal axis, and the α value at that time is shown on the vertical axis.

  As is clear from FIG. 10A, the α value fluctuates in a cycle of 60 °. The arrangement angle θ when the α value becomes the peak value is 30 °, 90 °, 150 °, or the like. The arrangement of the six second bolts 72 at the moment when the α value reaches the peak value is as shown in FIGS. 10B and 10C. For example, in FIGS. 10B and 10C, the arrangement angle θ at the position of the second bolt 72-1 is 30 °. 10B and 10C, the arrangement angle θ at the position of the second bolt 72-2 is 90 °. The arrangement of the second bolt 72 in FIGS. 10B and 10C is the same.

10B and 10C, the support angle θ _L formed by the bisector Lb of the two second bolts 72 marked with “〇” among the six second bolts 72 with respect to the second reference direction is , 90 ° or 270 °. The description of the bisector Lb is the same as the case where the number of the second bolts 72 is four. The description of the second reference direction is the same as the case where the number of the second bolts 72 is three. 90 ° is the smaller of the angles formed by the bisector Lb with respect to the second reference direction. 270 ° is the larger of the angles formed by the bisector Lb with respect to the second reference direction. Specifically, in FIG. 10B, the bisector Lb of the second bolt 72-1 adjacent the second bolt 72-6 is support angle theta _L which forms with respect to the second reference direction, 90 ° or 270 ° It is. In Figure 10C, support angle theta _L bisector Lb of the second bolt 72-3 adjacent the second bolt 72-4 forms with respect to the second reference direction is 90 ° or 270 °. Six arrangement of the second bolt 72 when the support angle theta _L support angle theta _L and when the 90 ° is 270 ° are the same. Thus, as α value becomes a peak value, a position supporting the angle theta _L is 90 °, it is preferable that the second bolt 72 of the six are arranged.

Further, as shown in FIG. 10A, in the range of 30 °, which is half of the 60 ° cycle, and the range including the peak value as the center, the α value is equal to or more than the average value. Therefore, it is preferable that the six second bolts 72 are arranged at positions where the support angle θ _L is within the range of 90 ° ± 15 °.

The case where the number of the second bolts 72 is four or six has been described above. However, in general, when the number is n, the n second bolts 72 are arranged at positions where the support angle θ _L is in the range of 90 ° ± (90 / n) °. Is preferred. According to this, the α value can be equal to or more than the average value.

  7B, 7C, 8B, 8C, 9B, 9C, 10B, and 10C, the one end surface 321a is orthogonal to the axial direction DRa at the position where the plurality of second bolts 72 of the compression mechanism 30 are arranged. This corresponds to an example of a virtual plane to be created.

The above-mentioned support angle theta _F, used in the provision of theta _L "applied load F" is the radial direction peak load F _p acting on the gravity F _G or drive shaft 14 acts on the compression mechanism portion 30. The peak load _Fp is a peak load under the condition in which the radial load received by the drive shaft 14 from the sub-bearing portion 16a is maximum among the operating conditions in which the compressor 10 is used. The direction of peak load F _p is applied is determined by calculation or the like from the specifications of the experiments and the compressor 10.

Further, in the above (ii) (iii), applied load F has been described several preferred arrangement of the second bolt 72 in the case of gravity F _G or radial peak load F _P. However, the acting load F may be an inertial force generated due to the vibration of the vehicle or the compressor. When the direction of the inertial force is clear, the α value is made to be equal to or more than the average value by disposing a plurality of second bolts 72 in the direction as described in (ii) and (iii) above. Can be.

(Third embodiment)
As shown in FIG. 11, in the present embodiment, a plurality of second bolts 73 are used instead of the plurality of second bolts 72 of the first embodiment. In the state where the main bearing member 36 and the first lid 122 sandwich the fixed scroll member 32, the plurality of second bolts 73 form three main bolts of the main bearing member 36, the fixed scroll member 32, and the first lid 122. Parts are fastened together. Hereinafter, the compressor 10 of the present embodiment will be specifically described.

  The first lid part 122 has a contact surface forming part 122b on which a contact surface 122a is formed. The contact surface 122a is a surface of the first lid 122 on the other side in the axial direction DRa. The contact surface 122a contacts one end surface 321a of the fixed scroll member 32. When an interposition such as a seal member is disposed between the one side end surface 321a and the first lid 122, the abutment surface 122a is in contact with the interposition. The contact surface forming portion 122b is located at a portion on the outer peripheral side of the first lid portion 122.

  The plurality of second bolts 73 have a male screw portion 73a and a head portion 73b. A bolt insertion hole 122c into which the plurality of second bolts 73 are inserted is formed in the contact surface forming portion 122b. The fixed scroll member 32 has a bolt insertion hole 327 into which the plurality of second bolts 73 are inserted. A plurality of female screw portions 367 corresponding to the male screw portions 73a of the plurality of second bolts 73 are formed in the bearing fixing portion 362.

  In assembling the components of the compressor 10 of the present embodiment, the centering of the compression mechanism 30 is performed as in the first embodiment. Thereafter, the motor unit 20 and the compression mechanism unit 30 are inserted into the housing main body 121 from one side of the housing main body 121 in the axial direction DRa.

  Thereafter, the first lid 122 is disposed on one side of the housing body 121 in the axial direction DRa. At this time, the contact surface 122a of the first lid 122 contacts one end surface 321a of the fixed scroll member 32. In this state, the plurality of second bolts 73 are inserted into the bolt insertion holes 122c and 327 and the female screw portion 367 from one side in the axial direction DRa with respect to the first lid portion 122. In a state where the fixed scroll member 32 is sandwiched between the bearing fixing portion 362 and the contact surface forming portion 122b by the plurality of second bolts 73, the main bearing member 36, the fixed scroll member 32, and the first lid portion The three parts 122 are fastened together. Thereby, the compression mechanism 30 is fixed to the housing 12.

  The other configuration of the compressor 10 of the present embodiment is the same as that of the first embodiment. According to the present embodiment, the effects achieved by the configuration common to the first embodiment can be obtained.

  Furthermore, according to the present embodiment, there is no need to provide the protrusion 60 of the first embodiment. Therefore, the shape of the housing main body 121 can be made simple. Thereby, the manufacturing cost of the housing 12 can be reduced.

  Further, according to the present embodiment, similarly to the compression mechanism 30, the motor unit 20 can be assembled to the housing main body 121 from one side in the axial direction DRa with respect to the housing main body 121. Thereby, the assemblability of the components of the compressor 10 can be improved.

  In this embodiment, the desired number and arrangement of the plurality of fastening bolts 70 described in the second embodiment can be applied. Thereby, the same effect as in the second embodiment can be obtained.

(Fourth embodiment)
As shown in FIG. 12, in the present embodiment, a step portion 80 that forms a step surface 81 is provided in the housing body 121 instead of the projecting portion 60 of the first embodiment.

  The housing main body 121 has a first inner peripheral surface 82, a second inner peripheral surface 83, and a step surface 81. The first inner peripheral surface 82 is an inner peripheral surface of the housing main body 121 at a portion of the housing main body 121 where the electric motor unit 20 is disposed. The first inner peripheral surface 82 has a cylindrical shape. The second inner peripheral surface 83 is located on one side in the axial direction DRa than the first inner peripheral surface 82. The second inner peripheral surface 83 has a cylindrical shape. The second inner peripheral surface 83 is an inner peripheral surface of the housing main body 121 at a portion of the housing main body 121 where the compression mechanism 30 is disposed. The outer diameter of the compression mechanism 30 is larger than the outer diameter of the electric motor 20. Therefore, the diameter of the second inner peripheral surface 83 is larger than the diameter of the first inner peripheral surface 82.

  The step surface 81 connects the first inner peripheral surface 82 and the second inner peripheral surface 83. The step surface 81 extends in a direction orthogonal to the axial direction DRa. The step surface 81 is in direct contact with the other end surface 362 b on the other side of the bearing fixing portion 362 of the main bearing member 36. Note that the step surface 81 may be in contact with the other end surface 362b via an interposition. Therefore, in the present embodiment, the step surface 81 corresponds to a contact surface that comes into contact with the end surface on the other side in the axial direction of the bearing fixing portion directly or via an inclusion. The step portion 80 corresponds to a contact surface forming portion on which a contact surface is formed.

  A plurality of female screw portions 84 corresponding to the male screw portions 72 a of the plurality of second bolts 72 are formed in the step portion 80.

  The housing main body 121 has a cup-like shape in which the side where the motor unit 20 is located is closed. That is, the housing main body 121 has a cylinder 121d and a bottom 121e. The cylindrical portion 121d has an opening 121a on one side in the axial direction DRa. The bottom part 121e is located on the other side in the axial direction DRa than the cylinder part 121d. The housing main body 121 is configured as a single-piece molded product in which the cylinder 121d and the bottom 121e are seamless.

  A cylindrical bearing forming portion 161 is provided on the bottom 121e. The bearing forming portion 161 forms an auxiliary bearing portion 16a on the inner peripheral side of the bearing forming portion 161. The bearing forming part 161 is formed integrally with the bottom part 121e. That is, the bearing forming portion 161 and the bottom portion 121e are formed as a seamlessly integrated product. For this reason, in this embodiment, it is not possible to adjust the position of the sub-bearing portion 16a with respect to the housing body 121.

  When the compression mechanism 30 is assembled to the housing main body 121, a gap δp for centering is formed between the outer peripheral surface 30 a of the compression mechanism 30 and the second inner peripheral surface 83 of the housing main body 121. Is formed. The dimension of the centering gap δp in the radial direction is the maximum dimension in the radial direction of a gap (not shown) between the main bearing 361a and the drive shaft 14, and the dimension between the sub-bearing 16a and the drive shaft 14. It is larger than the sum of the maximum dimension in the radial direction of the gap (not shown). The reason for this is that the size of the centering gap δp is larger than the size of the stacked coaxiality of the components constituting the compression mechanism 30, the main bearing 361a, and the sub-bearing 16a. is there.

  In assembling the components of the compressor 10 of the present embodiment, the centering of the compression mechanism 30 is performed as in the first embodiment. Thereafter, in assembling to the housing main body 121, the electric motor section 20 and the compression mechanism section 30 are inserted into the housing main body 121 from one side in the axial direction DRa of the housing main body 121.

  Then, the other end surface 362b of the main bearing member 36 is brought into contact with the step surface 81 of the housing main body 121. In this state, the plurality of second bolts 72 are inserted into the bolt insertion holes 327 and 366 and the female screw portion 84 from one side to the other side in the axial direction DRa. When the bearing fixing portion 362 is sandwiched between the step portion 80 and the fixed scroll member 32 by the plurality of second bolts 72, the main bearing member 36, the fixed scroll member 32, and the first lid portion 122 Tighten the three parts together. Thereby, the compression mechanism 30 is fixed to the housing 12. At this time, in the present embodiment, the compression mechanism 30 is fastened to the housing 12 by the plurality of second bolts 72 while the main bearing 361a and the sub-bearing 16a are aligned.

  After the compression mechanism 30 is assembled to the housing main body 121, the first lid 122 is fixed to the housing main body 121.

  The other configuration of the compressor 10 of the present embodiment is the same as that of the first embodiment. According to the present embodiment, the effects achieved by the configuration common to the first embodiment can be obtained.

  Furthermore, according to the present embodiment, when the compression mechanism 30 is assembled to the housing main body 121, the outer peripheral surface 30 a of the compression mechanism 30 and the second inner peripheral surface 83 of the housing main body 121 are located between the outer peripheral surface 30 a and the second inner peripheral surface 83. , A centering gap δp is formed. For this reason, even if the position of the auxiliary bearing portion 16a cannot be adjusted with respect to the housing main body 121, when the compression mechanism 30 is assembled to the housing main body 121, the position of the compression mechanism 30 is shifted in a direction perpendicular to the axial direction DRa. Can be adjusted. Thereby, the center of the main bearing 361a and the sub-bearing 16a can be aligned.

  Further, according to the present embodiment, a part of the bottom part 121e of the housing main body part 121 forms the auxiliary bearing part 16a. For this reason, the auxiliary bearing member 16 and the pedestal 17 of the first embodiment can be eliminated. As described above, according to the present embodiment, centering and assembling can be performed, and the number of parts can be reduced. For this reason, it is possible to reduce the cost without reducing the bearing reliability.

  By the way, unlike the present embodiment, when the cylindrical portion 121d and the bottom portion 121e of the housing body 121 are formed separately, the wall thickness for forming a bolt seat or the like for fastening the both with bolts is reduced. It is necessary to have the part 121d and the bottom part 121e.

  On the other hand, according to the present embodiment, the cylindrical portion 121d and the bottom portion 121e of the housing main body 121 are formed as a seamlessly integrated molded product. Therefore, there is no need for a wall such as a bolt seat for fastening the both parts by bolts, and the required rigidity can be obtained with a relatively small thickness. Therefore, the pressure resistance can be maintained while suppressing the weight of the housing 12.

(Other embodiments)
(1) The above embodiments are not irrelevant to each other, and can be combined as appropriate, unless a combination is clearly not possible. For example, in the fourth embodiment, as in the third embodiment, the plurality of second bolts 73 fasten three parts of the main bearing member 36, the fixed scroll member 32, and the first lid 122. You may. In the first and third embodiments, the housing body 121 may have the step 80 as in the fourth embodiment.

  (2) In each of the above embodiments, the number of the plurality of first bolts 71 and the number of the plurality of second bolts 72 and 73 are the same. 71 and the plurality of second bolts 72 and 73 were alternately arranged. However, when the number of the plurality of first bolts 71 is different from the number of the plurality of second bolts 72, 73, the first bolts 71 and the second bolts 72, 73 are alternately provided in some of the plurality of fastening bolts 70. It does not need to be arranged in. Further, in all of the plurality of fastening bolts 70, the first bolts 71 and the second bolts 72, 73 need not be arranged alternately. Furthermore, the layout of the plurality of fastening bolts 70 is not uniform in the radial direction and the circumferential direction within a range allowable in strength in view of the layout of other functional parts such as the refrigerant passage, the oil passage, and the rotation preventing mechanism. You may.

  (3) In each of the above embodiments, the fixed crank mechanism is employed as the crank mechanism for the orbiting movement of the orbiting scroll member. However, a driven crank mechanism may be employed as long as the relative inclination of the bearing portion is within a range allowable in terms of reliability.

  (4) In the first embodiment, the protruding portions 60 are arranged over the entire area of the inner peripheral surface 121c in the circumferential direction. However, each of the plurality of protrusions 60 may be arranged at intervals in the circumferential direction of the inner peripheral surface 120c.

  (5) In the above embodiments, the positions of the suction port 125 and the discharge port 126 in the housing 12 are specifically specified, but the present invention is not limited to this. The suction port 125 and the discharge port 126 may be provided in the housing 12 at positions other than the positions described in the above-described embodiment.

  (6) In the above embodiments, each of the main bearing portion 361a, the sub bearing portion 16a, and the eccentric bearing portion 342a is configured by a slide bearing. However, at least one of the main bearing portion 361a, the sub bearing portion 16a, and the eccentric bearing portion 342a may be configured with a bearing (for example, a ball bearing) other than the slide bearing.

  (7) In each of the above-described embodiments, the compressor 10 is configured such that the axis CL of the drive shaft 14 extends substantially in the horizontal direction, and the compression mechanism 30 and the electric motor 20 are arranged side by side in the substantially horizontal direction. It is an installation structure. However, the compressor 10 may have a vertical structure in which the axis CL of the drive shaft 14 extends substantially in the vertical direction DRv and the compression mechanism 30 and the electric motor 20 are arranged substantially in the vertical direction DRv. Good.

  (8) In each of the above embodiments, the compressor 10 is an inverter-integrated compressor in which the inverter 25 is integrally attached to the housing 12. However, the inverter 25 may be formed separately from the housing 12.

  (9) In each of the above embodiments, the compressor 10 is an electric compressor in which the compression mechanism 30 is driven using the electric motor 20 as a power source. However, the compressor 10 may have a configuration in which the compression mechanism 30 is driven using the internal combustion engine as a power source.

  (10) In each of the above embodiments, the refrigerant used in the refrigeration cycle apparatus 1 is carbon dioxide, but may be a CFC-based refrigerant.

  (11) The present invention is not limited to the above-described embodiment, but can be appropriately modified within the scope described in the claims, and includes various modifications and modifications within an equivalent range. In each of the above embodiments, it is needless to say that elements constituting the embodiments are not necessarily essential, unless otherwise clearly indicated as being essential or in principle considered to be clearly essential. No. In each of the above embodiments, when a numerical value such as the number, numerical value, amount, range, or the like of the constituent elements of the exemplary embodiment is mentioned, it is particularly limited to a specific number when it is clearly stated that it is essential and in principle. The number is not limited to the specific number unless otherwise specified. Further, in each of the above embodiments, when referring to the material, shape, positional relationship, and the like of the constituent elements, unless otherwise specified, and in principle, it is limited to a specific material, shape, positional relationship, and the like. It is not limited to the material, shape, positional relationship, and the like.

(Summary)
According to a first aspect shown in a part or all of the above embodiments, the compressor includes a scroll-type compression mechanism, a drive shaft, a housing, and a plurality of fastening bolts. The compression mechanism section has a fixed scroll member, an orbiting scroll member, and a bearing member. The plurality of fastening bolts include a plurality of first bolts and a plurality of second bolts. The plurality of first bolts fasten only two components of the fixed scroll member, the bearing member, and the housing member among the three components of the fixed scroll member, the bearing member, and the housing. The plurality of second bolts fasten the three parts together.

  According to the second aspect, the bearing member has a bearing fixing portion fixed to the fixed scroll member by a plurality of fastening bolts. The housing has a cylindrical housing body having an opening at least on one side in the axial direction. The housing body has a contact surface forming portion formed with a contact surface that is in contact with an end surface on the other side in the axial direction of the bearing fixing portion directly or via an interposition. The plurality of second bolts fasten the three parts together with the bearing fixing portion being sandwiched between the contact surface forming portion and the fixed scroll member.

  As described above, as a specific configuration of the first aspect, for example, the configuration of the second aspect can be adopted.

  According to the third aspect, a plurality of female screw portions corresponding to the male screw portions of the plurality of second bolts are formed in the contact surface forming portion. According to this, the compression mechanism is inserted into the housing body from one side in the axial direction toward the other side. Thereafter, the plurality of second bolts can be inserted into the fixed scroll member from one side in the axial direction to the other side. Therefore, it is easy to assemble the plurality of second bolts.

  According to the fourth aspect, the contact surface forming portion is a protruding portion that protrudes from the housing body to the drive shaft side. Thus, for example, the configuration of the fourth aspect can be adopted as a specific configuration of the second aspect.

  Further, according to the fifth aspect, the housing main body is located on the first inner peripheral surface and on one side in the axial direction with respect to the first inner peripheral surface, and has a diameter larger than the first inner peripheral surface. It has an inner peripheral surface, and a step surface connecting the first inner peripheral surface and the second inner peripheral surface. The contact surface is a step surface. The contact surface forming portion is a step portion that forms a step surface in the housing body. As described above, for example, the configuration according to the fifth aspect can be adopted as a specific configuration according to the second aspect.

  According to the sixth aspect, the bearing member has the bearing fixing portion fixed to the fixed scroll member by the plurality of fastening bolts. The housing has a cylindrical housing main body having an opening at least on one side in the axial direction, and a lid covering the opening at a position on one side in the axial direction with respect to the housing main body. The lid portion has a contact surface forming portion formed with a contact surface that is in contact with one end surface on one side in the axial direction of the fixed scroll member or an inclusion between the lid portion and the one end surface. The plurality of second bolts fasten the three components together in a state where the fixed scroll member is sandwiched between the bearing fixing portion and the contact surface forming portion.

  Thus, as a specific configuration of the first aspect, for example, the configuration of the sixth aspect can be adopted.

  Further, according to the seventh aspect, the bearing fixing portion is formed with a female screw portion corresponding to the male screw portion of the plurality of second bolts. According to this, the opening of the housing main body is covered with the housing lid after the compression mechanism is inserted into the housing main body from one side to the other side in the axial direction. Thereafter, a plurality of second bolts can be inserted from one side in the axial direction to the other side. Therefore, it is easy to assemble the plurality of second bolts.

  According to the eighth aspect, on the virtual plane orthogonal to the axial direction at the position where the plurality of second bolts are arranged in the compression mechanism, each of the plurality of second bolts is positioned on the axis of the drive shaft. They are arranged at equal intervals along the circumference of a circle centered on the position.

  According to this, the fastening force of the plurality of second bolts, that is, the axial force of the plurality of second bolts, is evenly generated in each radial direction when the center of the compression mechanism is the center of the circle. be able to. As a result, in a certain direction, the axial force of the plurality of second bolts is low, so that the compression mechanism and the housing may be displaced or the mutual parts may be locally deformed, and the Thus, it is possible to suppress the compression mechanism from relatively tilting.

  According to the ninth aspect, the number of the plurality of second bolts is three or more. According to this, the compression mechanism can be stably supported.

  According to the tenth aspect, the axis of the drive shaft extends in a direction crossing the direction of gravity. The number of the plurality of second bolts is an odd number. The number of the plurality of second bolts is n. The direction in which the gravity acting on the compression mechanism is indicated on the virtual plane starting from the center of the circle on the virtual plane is defined as a reference direction. On this imaginary plane, the angle formed by the line segment connecting the center of one of the second bolts and the center of the circle with respect to the reference direction is the support angle. At this time, the support angle of 0 ° ± (45 / n) ° is within the range of 180 ° ± (45 / n) °.

  According to this, the supporting force of the plurality of second bolts against the gravity acting on the compression mechanism can be increased.

  According to an eleventh aspect, the bearing is the first bearing. The compressor has a second bearing portion that rotatably supports the drive shaft inside the housing. The second bearing portion is arranged on a side opposite to the compression mechanism portion side with respect to the first bearing portion and apart from the first bearing portion. The number of the plurality of second bolts is an odd number. The number of the plurality of second bolts is n. In the operating conditions in which the compressor is used, the direction in which the peak load acts when the load in the radial direction received by the drive shaft from the second bearing portion is the maximum is defined by the center of the circle on an imaginary plane. The direction when shown on the virtual plane starting from is the reference direction. On this imaginary plane, the angle formed by the line segment connecting the center of one of the second bolts and the center of the circle with respect to the reference direction is the support angle. At this time, the support angle is within a range of 0 ° ± (45 / n) ° or 180 ° ± (45 / n) °.

  According to this, it is possible to increase the supporting force of the plurality of second bolts with respect to the radial peak load acting on the compression mechanism.

According to the twelfth aspect, the axis of the drive shaft extends in a direction intersecting the direction of gravity. The number of the plurality of second bolts is an even number. The number of the plurality of second bolts is n. The direction in which the direction of action of gravity acting on the compression mechanism is indicated with the center of the circle on the virtual plane as a starting point is defined as a reference direction. On a virtual plane, a bisector that bisects an angle formed by a line segment connecting the center of each of the two adjacent second bolts of the plurality of second bolts and the center of the circle is a reference direction. Is defined as a support angle (θ _L ). At this time, the support angle is within a range of 90 ° ± (90 / n) °.

  According to this, the supporting force of the plurality of second bolts against the gravity acting on the compression mechanism can be increased.

  According to the thirteenth aspect, the bearing is the first bearing. The compressor has a second bearing portion that rotatably supports the drive shaft inside the housing. The second bearing portion is arranged on a side opposite to the compression mechanism portion side with respect to the first bearing portion and apart from the first bearing portion. The number of the plurality of second bolts is an even number. The number of the plurality of second bolts is n. Among the operating conditions in which the compressor is used, the direction in which the peak load acts when the load in the radial direction that the drive shaft receives from the second bearing portion is maximized is defined by the axis of the drive shaft on a virtual plane. The direction indicated on the imaginary plane with the position as a starting point is defined as a reference direction. On a virtual plane, a bisector that bisects an angle formed by a line segment connecting the center of each of two adjacent second bolts of the plurality of second bolts and the position of the axis of the drive shaft, The angle formed with respect to the reference direction is defined as a support angle. At this time, the support angle is within a range of 90 ° ± (90 / n) °.

  According to this, it is possible to increase the supporting force of the plurality of second bolts with respect to the radial peak load acting on the compression mechanism.

  According to the fourteenth aspect, at least a part of the plurality of fastening bolts has the first bolts and the second bolts arranged alternately along the circumference. According to this, the first bolt and the second bolt can be arranged in a well-balanced manner.

  According to the fifteenth aspect, the housing body has a cylindrical portion having an opening on one side in the axial direction, and a bottom on the other side in the axial direction than the cylindrical portion. It is configured as a seamless integral molded product. The bearing is a first bearing. A part of the bottom part forms a second bearing part that rotatably supports the drive shaft. A gap is formed between the outer peripheral surface of the compression mechanism and the inner peripheral surface of the housing body. The radial dimension of this gap is the maximum radial dimension of the gap between the first bearing and the drive shaft, and the maximum radial dimension of the gap between the second bearing and the drive shaft. And greater than the sum.

  According to this, even when the position of the second bearing portion cannot be adjusted with respect to the housing main body, the position of the compression mechanism is adjusted in a direction perpendicular to the axial direction when assembling the compression mechanism to the housing main body. be able to. Thus, the first bearing portion and the second bearing portion can be aligned.

12 Housing 14 Drive shaft 30 Compression mechanism 32 Fixed scroll member 32
34 Orbiting scroll member 36 Bearing member 70 Plural fastening bolts 71 Plural first bolts 72 Plural second bolts

Claims (15)

A compressor that compresses and discharges the sucked refrigerant,
A scroll-type compression mechanism (30);
A drive shaft (14) for transmitting a driving force to the compression mechanism;
A housing (12) for housing the compression mechanism and the drive shaft;
A plurality of fastening bolts (70) for fastening the components of the compression mechanism,
The compression mechanism,
A fixed scroll member (32) fixed to the housing;
A orbiting scroll member (34) that is arranged alongside the fixed scroll member in the axial direction of the drive shaft and engages with the fixed scroll member to compress refrigerant when orbiting by the driving force of the drive shaft;
A bearing member (361a) for rotatably supporting the drive shaft, and a bearing member (36) fixed to the fixed scroll member by the plurality of fastening bolts;
The plurality of fastening bolts include a plurality of first bolts (71) and a plurality of second bolts (72, 73),
The plurality of first bolts fasten only two components of the fixed scroll member, the bearing member, and the housing member among the three components of the fixed scroll member, the bearing member, and the housing,
The compressor, wherein the plurality of second bolts fasten the three parts together. The bearing member has a bearing fixing portion (362) fixed to the fixed scroll member by the plurality of fastening bolts,
The housing has a cylindrical housing body (121) having an opening (121a) on at least one side in the axial direction,
The housing body has a contact surface (60a, 81) formed with a contact surface (60a, 81) that is in contact with an end surface (362b) of the bearing fixing portion on the other side in the axial direction, directly or via an interposition. A surface forming portion (60, 80);
2. The plurality of second bolts (72) fasten the three components together with the bearing fixing portion being sandwiched between the contact surface forming portion and the fixed scroll member. 3. A compressor according to claim 1.   The compressor according to claim 2, wherein a plurality of female screw portions (61, 84) corresponding to the male screw portions (72a) of the plurality of second bolts are formed in the contact surface forming portion.   4. The compressor according to claim 2, wherein the contact surface forming portion is a protrusion (60) that protrudes from the housing body toward the drive shaft. 5. The housing main body is located on a first inner peripheral surface (82) on the one side in the axial direction than the first inner peripheral surface, and has a second inner periphery larger in diameter than the first inner peripheral surface. A surface (83), a step surface (81) connecting the first inner peripheral surface and the second inner peripheral surface,
The contact surface is the step surface,
4. The compressor according to claim 2, wherein the contact surface forming portion is a step portion (80) that forms the step surface of the housing body. 5. The bearing member has a bearing fixing portion (362) fixed to the fixed scroll member by the plurality of fastening bolts,
The housing has a cylindrical housing body (121) having an opening (121a) on at least one side in the axial direction, and the opening at the one side in the axial direction with respect to the housing body. And a lid (122) that covers
The lid portion has one end surface (321a) of the one side in the axial direction of the fixed scroll member or a contact surface (122a) that comes into contact with an inclusion between the one end surface and the lid portion. A contact surface forming portion (122b) formed,
The plurality of second bolts (73) fasten the three components together in a state where the fixed scroll member is sandwiched between the bearing fixing portion and the contact surface forming portion. A compressor according to claim 1.   The compressor according to claim 6, wherein a female screw portion (367) corresponding to the male screw portion (73a) of the plurality of second bolts is formed in the bearing fixing portion.   On the virtual plane orthogonal to the axial direction at the position where the plurality of second bolts are arranged in the compression mechanism, each of the plurality of second bolts is positioned at the axis (CL) of the drive shaft. The compressor according to any one of claims 1 to 7, wherein the compressor is arranged at regular intervals along a circumference of a circle serving as a center (Op).   The compressor according to claim 8, wherein the number of the plurality of second bolts is three or more. The axis of the drive shaft extends in a direction crossing the direction of gravity,
The number of the plurality of second bolts is an odd number,
The number of the plurality of second bolts is n, and the direction of action of gravity (F _G ) acting on the compression mechanism is defined as the origin of the center (Op) of the circle on the virtual plane. With the direction shown above as a reference direction, the center (Ob3) of one of the plurality of second bolts (72-3) and the center of the circle (Op ) Is defined as the support angle (θ _F ) with respect to the reference direction,
The compressor according to claim 9, wherein the support angle is in a range of 0 ° ± (45 / n) ° or 180 ° ± (45 / n) °. The bearing is a first bearing,
The compressor has a second bearing portion (16a) that rotatably supports the drive shaft inside the housing,
The second bearing portion is disposed on a side opposite to the compression mechanism portion side with respect to the first bearing portion, and is separated from the first bearing portion,
The number of the plurality of second bolts is an odd number,
When the number of the plurality of second bolts is n and the operating condition in which the compressor is used is a peak under a condition in which a radial load received by the drive shaft from the second bearing portion is a maximum. The direction in which the load (F _P ) acts on the virtual plane starting from the center (Op) of the circle on the virtual plane is defined as a reference direction. A line connecting the center (Ob3) of one of the second bolts (72-3) and the center (O _P ) of the circle supports an angle formed with respect to the reference direction. Angle (θ _F )
The compressor according to claim 9, wherein the support angle is in a range of 0 ° ± (45 / n) ° or 180 ° ± (45 / n) °. The axis of the drive shaft extends in a direction crossing the direction of gravity,
The number of the plurality of second bolts is an even number,
The number of said plurality of second bolt is n this, when the direction of gravity (F _G) acting on the compression mechanism portion, showing the center of the circle on the imaginary plane (Op) starting , The center (Ob1, Ob4) of each of two adjacent second bolts (72-1, 72-4) among the plurality of second bolts and the circle on the virtual plane. When the bisector (Lb) bisecting the angle formed by the line segment connecting the center (O _P ) with the center direction (O _P ) is defined as the support angle (θ _L ) with respect to the reference direction,
The compressor according to claim 9, wherein the support angle is in a range of 90 ° ± (90 / n) °. The bearing is a first bearing,
The compressor has a second bearing portion (16a) that rotatably supports the drive shaft inside the housing,
The second bearing portion is disposed on a side opposite to the compression mechanism portion side with respect to the first bearing portion, and is separated from the first bearing portion,
The number of the plurality of second bolts is an even number,
When the number of the plurality of second bolts is n and the operating condition in which the compressor is used is a peak under a condition in which a radial load received by the drive shaft from the second bearing portion is a maximum. The direction in which the load (F _P ) acts on the virtual plane starting from the center (Op) of the circle on the virtual plane is defined as a reference direction. formed by a line connecting the said center of the respective center (Ob1, Ob4) and the circle of the two second bolts adjacent among the plurality of second bolts (72-1,72-4) _{(O P)} When the angle formed by a bisector that bisects the angle with respect to the reference direction is a support angle (θ _L ),
The compressor according to claim 9, wherein the support angle is in a range of 90 ° ± (90 / n) °.   The compression according to any one of claims 8 to 13, wherein at least a part of the plurality of fastening bolts has the first bolts and the second bolts alternately arranged along the circumference. Machine. The housing body has a tubular portion (121d) having the opening and a bottom (121e) on the other side in the axial direction than the tubular portion, and the tubular portion and the bottom are seamlessly integrated. It is configured as a molded product,
The bearing is a first bearing,
A part of the bottom part forms a second bearing part (16a) that rotatably supports the drive shaft,
A maximum radial dimension of a gap between the first bearing and the drive shaft is provided between an outer peripheral surface (30a) of the compression mechanism and an inner peripheral surface (83) of the housing body. The gap (δp) having a dimension in the radial direction larger than the sum of the maximum dimension in the radial direction of the gap between the second bearing portion and the drive shaft is formed. The compressor as described.

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