EP3489514B1 - Bidirectional-rotation-type scroll compressor - Google Patents

Bidirectional-rotation-type scroll compressor Download PDF

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Publication number
EP3489514B1
EP3489514B1 EP17841518.8A EP17841518A EP3489514B1 EP 3489514 B1 EP3489514 B1 EP 3489514B1 EP 17841518 A EP17841518 A EP 17841518A EP 3489514 B1 EP3489514 B1 EP 3489514B1
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EP
European Patent Office
Prior art keywords
driving side
bearing
driving
driven
driven side
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Active
Application number
EP17841518.8A
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German (de)
English (en)
French (fr)
Other versions
EP3489514A4 (en
EP3489514A1 (en
Inventor
Takuma YAMASHITA
Takahide Ito
Makoto Takeuchi
Keita KITAGUCHI
Hirofumi Hirata
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Mitsubishi Heavy Industries Ltd
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Mitsubishi Heavy Industries Ltd
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Publication of EP3489514A4 publication Critical patent/EP3489514A4/en
Publication of EP3489514A1 publication Critical patent/EP3489514A1/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
    • F04C18/023—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where both members are moving
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/50—Bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/50—Bearings
    • F04C2240/52—Bearings for assemblies with supports on both sides
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/60—Shafts

Definitions

  • the present invention relates to a co-rotating scroll compressor.
  • co-rotating scroll compressors have been known (see PTL 1).
  • This includes a driving side scroll and a driven side scroll that rotates synchronously with the driving side scroll, and offsets a driven shaft that supports the rotation of the driven side scroll by a revolute radius, with respect to a drive shaft that rotates the driving side scroll, and rotates the drive shaft and the driven shaft at a same angular velocity in a same direction.
  • thermal stress may be generated in the scroll part.
  • the present invention has been made in view of such circumstances, and an object thereof is to provide a co-rotating scroll compressor capable of alleviating deformation caused by a centrifugal force generated in a scroll part.
  • Another object of the present invention is to provide the co-rotating scroll compressor capable of alleviating thermal stress generated in the scroll part.
  • a co-rotating scroll compressor of the present invention employs the following solutions.
  • the co-rotating scroll compressor includes, a driving side scroll member rotatably driven by a drive part, having a plurality of spiral driving side wall bodies installed with a predetermined angular interval around the center of a driving side end plate, a driven side scroll member installed with the predetermined angular interval around the center of a driven side end plate, having the number of spiral driven side wall bodies corresponding to each of the driving side wall bodies, and forming compression spaces by engaging each of the driven side wall bodies with the corresponding driving side wall bodies, a synchronous driving mechanism transmitting driving force from the driving side scroll member to the driven side scroll member so that the driving side scroll member and the driven side scroll member synchronously revolve, a first driving side bearing and a second driving side bearing rotatably supporting a shaft part at one end side and the other end side in an axial direction of the driving side scroll member, and a first driven side bearing and a second driven side bearing rotatably supporting the shaft part at one end side and the other end side in an axial direction of the driven side
  • Each of the driving side wall bodies arranged with the predetermined angular interval around the center of the end plate of the driving side scroll member is engaged with the corresponding driven side wall body of the driven side scroll member.
  • a plurality of pairs each including one driving side wall body and one driven side wall body are provided, and a scroll compressor having the wall body formed by a plurality of spirals is constituted.
  • the driving side scroll member is rotatably driven by the drive part, and the driving force transmitted to the driving side scroll member is transmitted to the driven side scroll member via the synchronous driving mechanism.
  • the driven side scroll member rotates and performs rotation with respect to the driving side scroll member in the same direction at the same angular speed.
  • the co-rotating scroll compressor is provided in which both the driving side scroll member and the driven side scroll member rotate.
  • the first driving side bearing and the second driving side bearing rotatably support the shaft parts on one end side and the other end side in the axial direction.
  • the rotation of the driving side scroll member generates a centrifugal force to deform the driving side wall body of the driving side scroll member radially outward.
  • the radially outward deformation of the outer peripheral side of the driving side scroll member tends to cause the driving side scroll member to deform to decrease a distance to axial direction between the shaft part supported by the first driving side bearing and the shaft part supported by the second driving side bearing. Allowing such deformation further increases the deformation radially outward on the outer peripheral side of the driving side scroll member.
  • a preload is applied to the shaft part so that an axial clearance in the second driving side bearing direction is eliminated in the first driving side bearing
  • a preload is applied to the shaft part so that an axial clearance in the first driving side bearing direction is eliminated in the second driving side bearing.
  • the first driven side bearing and the second driven side bearing rotatably support the shaft parts on one end side and the other end side in the axial direction.
  • the rotation of the driven side scroll member generates the centrifugal force to deform the driven side wall body of the driven side scroll member radially outward.
  • the radially outward deformation of the outer peripheral side of the driven side scroll member tends to cause the driven side scroll member to deform to decrease a distance to axial direction between the shaft part supported by the first driven side bearing and the shaft part supported by the second driven side bearing. Allowing such deformation further increases the deformation radially outward on the outer peripheral side of the driven side scroll member.
  • a preload is applied to the shaft part so that an axial clearance in the second driven side bearing direction is eliminated in the first driven side bearing and a preload is applied to the shaft part so that an axial clearance in the first driven side bearing direction is eliminated in the second driven side bearing.
  • the co-rotating scroll compressor according to the present invention includes a driving side support member arranged via the driven side end plate, fixed to a distal end side in the axial direction of the driving side wall body and rotates together with the driving side scroll member and a driven side support member arranged via the driving side end plate, fixed to a distal end side in the axial direction of the driven side wall body and rotates together with the driven side scroll member, and the first driving side bearing supports the shaft part of the driving side scroll member, the second driving side bearing supports the shaft part of the driving side support member, the first driven side bearing supports a shaft part of the driven side support member, and the second driven side bearing supports the shaft part of the driven side scroll member.
  • the shaft part of the driving side scroll member is supported by the first driving side bearing and the shaft part of the driving side support member is supported by the second driving side bearing. Further, as described above, it is constituted that applying a preload to the first driving side bearing and the second driving side bearing suppresses the deformation in which the distance to axial direction between both the shaft parts supported by each of the driving side bearings decreases. Therefore, it is possible to suppress a fixing part of the distal end of the wall body of the driving side scroll member and the driving side support member from being deformed radially outward due to the centrifugal force.
  • the shaft part of the driven side support member is supported by the first driven side bearing and the shaft part of the driven side scroll member is supported by the second driven side bearing. Further, as described above, it is constituted that applying a preload to the first driven side bearing and the second driven side bearing suppresses the deformation in which the distance to axial direction between both the shaft parts supported by each of the driven side bearings decreases. Therefore, it is possible to suppress the fixing part of the distal end of the wall body of the driven side scroll member and the driven side support member from being deformed radially outward due to the centrifugal force.
  • the distal end side of the driving side wall body and the driving side support member are fixed to allow displacement in the axial direction
  • each of the shaft parts is supported by a first driving side bearing and a second driving side bearing, to allow an increase in the distance between the shaft part supported by the first driving side bearing and the shaft part supported by the second driving side bearing
  • the distal end of the driven side wall body and the driven side support member are fixed to allow the displacement in the axial direction
  • each of the shaft parts is supported by the first driven side bearing and the second driven side bearing, to allow the increase in the distance between the shaft part supported by the first driven side bearing and the shaft part supported by the second driven side bearing.
  • the increase of temperature during the operation in the co-rotating scroll compressor tends to cause the driving side scroll member and the driving support member to thermally expand, and deform to increase the distance to axial direction between both the shaft parts supported by each of the driving side bearings.
  • the restraint of the deformation leads to the increase in thermal stress generated in the driving side scroll member and the driving side support member. Therefore, the distal end side of the driving side wall body and the driving side support member are fixed to allow the displacement in the axial direction, and each of the shaft parts is supported by the first driving side bearing and the second driving side bearing, to allow the increase in the distance between both the shaft parts supported by each of the driving side bearings.
  • the distance between both the shaft parts supported by each of the driving side bearings can be increased according to the thermal expansion, so that the generation of the thermal stress can be suppressed.
  • the distal end side of the driving side wall body and the driving side support member may be slidably fixed by pins to allow the displacement in the axial direction.
  • a preload direction of each driving side bearing may be set to cause the distal end side of the driving side wall body and the driving side support member to be displaceable in a direction in which the distance between both shaft parts supported by each driving side bearing increases.
  • the increase of temperature during the operation in the co-rotating scroll compressor tends to cause the driven side scroll member and the driven support member to thermally expand, and deform to increase the distance to axial direction between both the shaft parts supported by each of the driven side bearings.
  • the restraint of the deformation leads to the increase in the thermal stress generated in the driven side scroll member and the driven side support member. Therefore, the distal end side of the driven side wall body and the driven side support member are fixed to allow the displacement in the axial direction, and each of the shaft parts is supported by the first driven side bearing and the second driven side bearing, to allow the increase in the distance between both the shaft parts supported by each of the driven side bearings.
  • the distance between both the shaft parts supported by each of the driven side bearings can be increased according to the thermal expansion, so that the generation of the thermal stress can be suppressed.
  • the distal end side of the driven side wall body and the driven side support member may be slidably fixed by pins to allow the displacement in the axial direction.
  • the preload direction of each driven side bearing may be set to cause the distal end side of the driven side wall body and the driven side support member to be displaceable in a direction in which the distance between both shaft parts supported by each driven side bearing increases.
  • the driving side scroll member including a first driving side scroll part having the first driving side end plate and the first driving side wall body, driven by the drive part, a second driving side scroll part having a second driving side end plate and a second driving side wall body, and a fixed portion of wall fixing the first driving side wall body and the second driving side wall body in a state in which the distal ends of the first driving side wall body and the second driving side wall body in the axial direction face each other
  • the driven side scroll member including a first driven side wall body provided on one side face of the driven side end plate, engaged with the first driving side wall body, and a second driven side wall body provided on the other side face of the driven side end plate, engaged with the second driving side wall body, a first support member arranged via the first driving side end plate, fixed to a distal end side in the axial direction of the first driven side wall body and rotating together with the first driven side wall body and a second support member arranged via the second driving side end plate, fixed to the distal end
  • the shaft part of the first driving side scroll part is supported by the first driving side bearing and the shaft part of the second driving side scroll part is supported by the second driving side bearing. Further, as described above, it is constituted that applying a preload to the first driving side bearing and the second driving side bearing suppresses the deformation in which the distance to axial direction between both the shaft parts supported by each of the driving side bearings decreases. Therefore, it is possible to suppress the fixed portion of wall of the driving side scroll member from being deformed radially outward due to the centrifugal force.
  • the shaft part of the first support member is supported by the first driven side bearing and the shaft part of the second support member is supported by the second driven side bearing. Further, as described above, it is constituted that applying a preload to the first driven side bearing and the second driven side bearing suppresses the deformation in which the distance to axial direction between both the shaft parts supported by each of the driven side bearings decreases. Therefore, it is possible to suppress the fixing part of the distal end of each driven side wall body and each of the driven side support members from being deformed radially outward due to the centrifugal force.
  • the fixed portion of wall is fixed to allow the displacement in the axial direction
  • each of the shaft parts is supported by a first driving side bearing and a second driving side bearing, to allow the increase in the distance between the shaft part supported by the first driving side bearing and the shaft part supported by the second driving side bearing
  • the distal end of each of the driven side wall bodies and each of the support members is fixed to allow the displacement in the axial direction
  • each of the shaft parts is supported by a first driven side bearing and a second driven side bearing, to allow the increase in the distance between the shaft part supported by the first driven side bearing and the shaft part supported by the second driven side bearing.
  • the increase of temperature during the operation in the co-rotating scroll compressor tends to cause the driving side scroll member to thermally expand, and deform to increase the distance to axial direction between both the shaft parts supported by each of the driving side bearings.
  • the restraint of the deformation leads to the increase in the thermal stress generated in the driving side scroll member. Therefore, the fixed portion of wall is fixed to allow the displacement in the axial direction, and each of the shaft parts is supported by the first driving side bearing and the second driving side bearing, to allow the increase in the distance between both the shaft parts supported by each of the driving side bearings.
  • the distance between both the shaft parts supported by each of the driving side bearings can be increased according to the thermal expansion, so that the generation of the thermal stress can be suppressed.
  • a pin is used to allow the displacement in the axial direction.
  • the preload direction of each driving side bearing may be set to be displaceable in the direction in which the distance between both shaft parts supported by each driving side bearing increases.
  • the increase of temperature during the operation in the co-rotating scroll compressor tends to cause the driven side scroll member and the driven side support member to thermally expand, and deform to increase the distance to axial direction between both the shaft parts supported by each of the driven side bearings.
  • the restraint of the deformation leads to the increase in the thermal stress generated in the driven side scroll member and each of the support members. Therefore, the distal end of each driven side wall body and each of the support members are fixed to allow the displacement in the axial direction, and each of the shaft parts is supported by the first driven side bearing and the second driven side bearing, to allow the increase in the distance between both the shaft parts supported by each of the driven side bearings.
  • the distance between both the shaft parts supported by each of the driven side bearings can be increased according to the thermal expansion, so that the generation of the thermal stress can be suppressed.
  • each driven side wall body and each of the support members may be fixed by pins to allow it to displace in the axial direction.
  • the preload direction of each driven side bearing may be set to be displaceable in a direction in which the distance between both shaft parts supported by each driven side bearing increases.
  • the co-rotating scroll compressor according to the present invention includes a first housing having a bearing fixing part to which the first driving side bearing and the first driven side bearing are fixed, and a second housing contacted against and fixed to the first housing in the axial direction, and having a bearing fixing part to which the second driving side bearing and the second driven side bearing are fixed. Contacting the first housing and the second housing each other in the axial direction to be fixed applies a preload to both the driving side bearings and/or both the driven side bearings.
  • the first driving side bearing is provided on the shaft part on the opposite side sandwiching the drive part as seen from the driving side end plate of the driving side scroll member.
  • the first driving side bearing is provided on the shaft part on the opposite side sandwiching the drive part (for example, an electric motor) as seen from the driving side end plate.
  • the drive part for example, an electric motor
  • a preload is applied to the shaft part to eliminate an axial clearance between each of the bearings, so that it is possible to alleviate deformation caused by the centrifugal force generated in the scroll member.
  • Fixing to allow the displacement in the axial direction of the fixing part and allowance of the increase in the distance between the shafts supported by each of the bearings can suppress the generation of the thermal stress.
  • Fig. 1 shows a co-rotating scroll compressor 1A.
  • the co-rotating scroll compressor 1A can be used as a supercharger for compressing combustion air (fluid) supplied to an internal combustion engine such as vehicle engines.
  • the co-rotating scroll compressor 1A includes a housing 3, a motor (drive part) 5 housed on one end side of the housing 3, a driving side scroll member 70 and a driven side scroll member 90 housed on the other end side of the housing 3 .
  • the housing 3 has a substantially cylindrical shape and includes a motor housing part (first housing) 3a housing the motor 5 and a scroll housing part (second housing) 3b housing the scroll members 7 and 9.
  • Cooling fins 3c cooling the motor 5 are provided on the outer periphery of the motor housing part 3a.
  • a discharge port 3d discharging compressed air is formed at an end part of the scroll housing part 3b.
  • the housing 3 is provided with an air intake port for drawing in air.
  • the scroll housing part 3b of the housing 3 is divided by a dividing face P positioned substantially at the center in the axial direction of the scroll members 70 and 90.
  • the housing 3 is provided with a flange part (fastening part) 30 protruding outward at a predetermined position in a circumferential direction.
  • Bolts 32 as fastening means are fixed through the flange part 30 so that the dividing face P is fastened.
  • the electric power supplied from the power supply source which is not shown drives the motor 5.
  • An instruction from a control unit which is not shown controls rotation of the motor.
  • a stator 5a of the motor 5 is fixed to the inner peripheral side of the housing 3.
  • a rotor 5b of the motor 5 rotates around a driving side rotation axis CL1.
  • a drive shaft 6 extending on the driving side rotation axis CL1 is connected to the rotor 5b.
  • the drive shaft 6 is connected to a first driving side shaft part 7c of the driving side scroll member 70.
  • a rear end bearing 17 that rotatably supports the drive shaft 6 between the drive shaft 6 and the housing 3 is provided.
  • the driving side scroll member 70 includes a first driving side scroll part 71 on the motor 5 side and a second driving side scroll part 72 on the discharge port 3d side.
  • the first driving side scroll part 71 includes a first driving side end plate 71a and a first driving side wall body 71b.
  • the first driving side end plate 71a is connected to the first driving side shaft part 7c connected to the drive shaft 6, and extends in a direction orthogonal to the driving side rotation axis CL1.
  • the first driving side shaft part 7c is rotatably provided with respect to the housing 3 via a first driving side bearing 11 which is an angular ball bearing.
  • the first driving side end plate 71a has a substantially disk shape in a plan view. As shown in Fig. 2 , three, that is, triple spirals of the first driving side wall bodies 71b which are formed to spiral are provided on the first driving side end plate 71a. The first driving side wall bodies 71b having triple spirals are arranged at equal intervals around the driving side rotation axis CL1. Winding end parts 71e of the first driving side wall bodies 71b are not fixed to the other wall parts, but are independent from each other. That is, no wall part is provided to reinforce the first driving side wall bodies 71b by connecting the winding end parts 71e together.
  • the second driving side scroll part 72 includes a second driving side end plate 72a and a second driving side wall body 72b.
  • the second driving side wall body 72b has triple spirals similarly to the above-described first driving side wall body 71b (see Fig. 2 ).
  • a second driving side shaft part 72c extending in a direction of the driving side rotation axis CL1 is connected to the second driving side end plate 72a.
  • the second driving side shaft part 72c is rotatably provided with respect to the housing 3 via a second driving side bearing 14 which is the angular ball bearing.
  • a preload member 14a such as a nut, a disk spring is provided on the side of the inner ring of the second driving side bearing 14.
  • the preload member 14a is attached to the second driving side shaft part 72c and is fixed to press the inner ring of the second driving side bearing 14 toward the first driving side bearing 11 side.
  • an axial clearance between the enlarged diameter shoulder part of the second driving side shaft part 72c and the side face of the second driving side bearing 14 is made zero.
  • a discharge port 72d is formed on the second driving side shaft part 72c along the driving side rotation axis CL1.
  • the first driving side scroll part 71 and the second driving side scroll part 72 are fixed in a state in which the distal ends (free ends) of the wall bodies 71b and 72b face each other.
  • the first driving side scroll part 71 and the second driving side scroll part 72 are fixed to each other by pins (fixed portion of wall) 31 fastened to the flange parts 73 provided at a plurality of positions in the circumferential direction to protrude outward in the radial direction. Fixing by the pin 31 allows the first driving side scroll part 71 and the second driving side scroll part 72 to move in the direction away from each other along the axial direction (horizontal direction in Fig. 1 ).
  • the driven side scroll member 90 has a driven side end plate 90a provided substantially at the center in the axial direction (horizontal direction in the drawing).
  • a through hole 90h is formed in the center of the driven side end plate 90a so that the compressed air flows to the discharge port 72d.
  • driven side wall bodies 91b and 92b are provided, respectively.
  • the first driven side wall body 91b installed on the motor 5 side from the driven side end plate 90a is engaged with the first driving side wall body 71b of the first driving side scroll part 71
  • the second driven side wall body 92b installed on the discharge port 3d side from the driven side end plate 90a is engaged with the second driving side wall body 72b of the second driving side scroll part 72.
  • the driven side wall bodies 9b having triple spirals are arranged at equal intervals around the driven side rotation axis CL2.
  • the second driven side wall body 92b has also the same configuration.
  • a first support member 33 and a second support member 35 are provided on both ends of the driven side scroll member 90 in the axial direction (horizontal direction in the drawing).
  • the first support member 33 is arranged on the motor 5 side and the second support member 35 is arranged on the discharge port 3d side.
  • the first support member 33 is fixed to the distal end (free end) of the first driven side wall body 91b by a pin 25a
  • the second support member 35 is fixed to the distal end (free end) of the second driven side wall body 92b by a pin 25b. Fixing the pins 25a and 25b causes the wall bodies 91b and 92b and the support members 33 and 35 to move in the direction away from each other along the axial direction (horizontal direction in Fig. 1 ).
  • first support member shaft part 33a On the center shaft side of the first support member 33, there is provided a first support member shaft part 33a, which is fixed to the housing 3 via a first support member bearing (first driven side bearing) 37 which is the angular ball bearing.
  • second support member shaft part 35a On the center shaft side of the second support member 35, there is provided a second support member shaft part 35a, which is fixed to the housing 3 via a second support member bearing (second driven side bearing) 38 which is the angular ball bearing.
  • a pin ring mechanism (synchronous driving mechanism) 15 is provided between the first support member 33 and the first driving side end plate 71a. That is, a ring member 15a is provided on the first driving side end plate 71a, and a pin member 15b is provided on the first support member 33.
  • the pin ring mechanism 15 is used as the synchronous driving mechanism transmitting driving force from the driving side scroll member 70 to the driven side scroll member 90 so that both the scroll members 70 and 90 synchronously revolve.
  • a pin ring mechanism (synchronous driving mechanism) 15 is provided between the second support member 35 and the second driving side end plate 72a. That is, a ring member 15a is provided on the second driving side end plate 72a, and a pin member 15b is provided on the second support member 35.
  • the pin ring mechanism 15 is used as the synchronous driving mechanism transmitting the driving force from the driving side scroll member 70 to the driven side scroll member 90 so that both the scroll members 70 and 90 synchronously revolve.
  • preload directions of each of the bearings 11, 14, 37 and 38 are shown.
  • the preload direction (contact angle caused by a preload) is indicated by black thick solid lines on the bearings 11, 14, 37 and 38.
  • a preload is applied to the second driving side shaft part 72c by the preload member 14a so that the clearance on the inner ring side of the first driving side bearing 11 side (right side in Fig. 4 ) becomes zero. That is, the right side face of the inner ring of the second driving side bearing 14 contacts against the left side face of the enlarged diameter part of the second driving side shaft part 72c.
  • a preload is applied to the first driving side shaft part 7c so that the clearance on the inner ring side of the second driving side bearing 14 side (left side in Fig. 4 ) becomes zero. That is, the left side face of the inner ring of the first driving side bearing 11 contacts against the right side face of the enlarged diameter part of the first driving side shaft part 7c.
  • the first driving side bearing 11 and the second driving side bearing 14 are in a DB (back surface combination) preloading relation.
  • the restraint in the axial direction of the driving side scroll member 70 by each of the inner rings of the first driving side bearing 11 and the second driving side bearing 14 suppresses deformation in the direction in which the first driving side shaft part 7c and the second driving side shaft part 72c of the driving side scroll member 70 approaches each other.
  • the application of the DB preload allows the deformation in the direction in which the distance between the inner ring of the first driving side bearing 11 and the inner ring of the second driving side bearing 14 increases.
  • a preload is applied to the first support member shaft part 33a so that the outer ring is urged toward the second support member bearing 38 (left direction in Fig. 4 ) in the first support member bearing 37.
  • a preload is applied to the second support member shaft part 35a so that the outer ring is urged toward the first support member bearing 37 (right direction in Fig. 4 ) in the second support member bearing 38.
  • the first support member bearing 37 and the second support member bearing 38 are in a DF (front face combination) preloading relation.
  • a preload is applied to the first support member bearing 37 and the second support member bearing 38 when the motor housing part 3a of the housing 3 and the scroll housing part 3b are assembled by the bolts 32.
  • the co-rotating scroll compressor 1A having the above configuration operates as follows.
  • the rotation of the drive shaft 6 around the driving side rotation axis CL1 by the motor 5 also rotates the first driving side shaft part 7c connected to the drive shaft 6 so that the driving side scroll member 70 rotates around the driving side rotation axis CL1.
  • the rotation of the driving side scroll member 70 transmits the driving force from each of the support members 33 and 35 to the driven side scroll member 90 via the pin ring mechanism 15 and rotates the driven side scroll member 90 around the driven side rotation axis CL2.
  • the movement of the pin member 15b of the pin ring mechanism 15 in contact with the ring member 15a causes both the scroll members 70 and 90 to relatively revolve.
  • both the scroll members 70 and 90 causes the air sucked from the suction port of the housing 3 to be sucked from the outer peripheral sides of both the scroll members 70 and 90 and taken into the compression chambers formed by both the scroll members 70 and 90.
  • the compression chamber formed by the first driving side wall body 71b and the first driven side wall body 91b, and the compression chamber formed by the second driving side wall body 72b and the second driven side wall body 92b are compressed separately. As the taken air moves toward the center side in each compression chamber, the volume decreases, and accordingly the air is compressed.
  • the air compressed by the first driving side wall body 71b and the first driven side wall body 91b passes through the through hole 90h formed in the driven side end plate 90a, and combines with the air compressed by the second driving side wall body 72b and the second driven side wall body 92b.
  • the combined air passes through the discharge port 72d, and is discharged from the discharge port 3d of the housing 3 to the outside.
  • the discharged compressed air is guided to an internal combustion engine which is not shown and is used as combustion air.
  • the first driving side bearing 11 and the second driving side bearing 14 rotatably support each of the shaft parts 7c and 72c.
  • the rotation of the driving side scroll member 70 generates a centrifugal force to deform the driving side wall bodies 71b and 72b of the driving side scroll member 70 radially outward (see Fig. 5 ).
  • the radially outward deformation of the outer peripheral side of the driving side scroll member 70 tends to cause the driving side scroll member 70 to deform to decrease a distance to axial direction between the shaft part 7c supported by the first driving side bearing 11 and the shaft part 72c supported by the second driving side bearing 14, as shown by a broken line in Fig. 5(a) .
  • Such allowance of the deformation further increases the deformation radially outward on the outer peripheral side of the driving side scroll member 70.
  • a preload is applied to the first driving side shaft part 7c so that an axial clearance in the second driving side bearing 14 direction is eliminated in the first driving side bearing 11 and a preload is applied to the second driving side shaft part 72c so that an axial clearance in the first driving side bearing 11 direction is eliminated in the second driving side bearing 14.
  • the distal ends of the first driving side wall body 71b and the second driving side wall body 72b is fixed to each other by the pin 31 to allow displacement in the axial direction, and both the shaft parts 7c and 72c are supported by each of the driving side bearings 11 and 14 to allow the increase in the distance between both the shaft parts 7c and 72c supported by the driving side bearings 11 and 14, that is, to allow the increase in the distance between the inner ring of the first driving side bearing 11 and the inner ring of the second driving side bearing 14.
  • the distance between both the shaft parts 7c and 72c supported by each of the driving side bearings 11 and 14 can be increased according to the thermal expansion, so that the generation of the thermal stress can be suppressed.
  • the preload directions of the first support member bearing 37 and the second support member bearing 38 may be set.
  • double tooth that is, two wall bodies of 71b, 72b, 91b and 92b are provided for each of the driving side scroll member 70 and the driven side scroll member 90, but in this embodiment, it is different in that one tooth, that is, one wall body is provided for each of the driving side scroll member 7 and the driven side scroll member 9.
  • the same reference numerals are given to the same configurations as those of the first embodiment, and the description thereof is omitted.
  • the co-rotating scroll compressor 1B includes a driving side scroll member 7 housed in a motor housing part 3a of the housing 3 and a driven side scroll member 9 housed in the scroll housing part 3b.
  • the driving side scroll member 7 has a driving side end plate 7a and a spiral driving side wall body 7b installed on one side of the driving side end plate 7a.
  • the driving side end plate 7a is connected to the driving side shaft part 7c connected to the drive shaft 6 and extends in the direction orthogonal to the driving side rotation axis line CL1.
  • the driving side shaft part 7c is rotatably provided with respect to the housing 3 via a driving side bearing 11 which is the angular ball bearing.
  • the driving side end plate 7a has a substantially disk shape in a plan view.
  • the driving side scroll member 7 provided with three, that is, triple spirals of the driving side wall bodies 7b which are formed to spiral.
  • the driving side wall bodies 7b having triple spirals are arranged at equal intervals around the driving side rotation axis CL1.
  • the driven side scroll member 9 is arranged to engage with the driving side scroll member 7, and has a driven side end plate 9a and a spiral shaped driven side wall body 9b installed on one side of the driven side end plate 9a.
  • a driven side shaft part 9c extending in the direction of the driven side rotational axis CL2 is connected to the driven side end plate 9a.
  • the driven side shaft part 9c is rotatably provided with respect to the housing 3, via a driven side bearing 13 which is the angular ball bearing.
  • the driven side end plate 9a has a substantially disk shape in a plan view. Like the first driven side wall body 91b shown in Fig. 3 , the driven side scroll member 9 is provided with three, that is, triple spirals of the driven side wall bodies 9b which are formed to spiral. The driven side wall bodies 9b having triple spirals are arranged at equal intervals around the driven side rotation axis CL2. A discharge port 9d discharging the compressed air is formed substantially at the center of the driven side end plate 9a. The discharge port 9d communicates with a discharge port 3d formed in the housing 3.
  • a driving side support member 20 is fixed to the distal end (free end) of the driving side wall body 7b of the driving side scroll member 7 via a pin 24a.
  • a driven side scroll member 9 is sandwiched between the driving side support member 20 and the driving side scroll member 7. Therefore, the driven side end plate 9a is arranged to face the driving side support member 20.
  • the driving side support member 20 has a driving side support member shaft part 20a on the center side, which is rotatably attached to the housing 3 via a driving side support member bearing 26 which is the angular ball bearing. As a result, the driving side support member 20 rotates around the driving side rotation axis CL1 like the driving side scroll member 7.
  • a pin ring mechanism 15 is provided between the driving side support member 20 and the driven side end plate 9a.
  • the pin ring mechanism 15 is used as the synchronous driving mechanism transmitting the driving force from the driving side scroll member 7 to the driven side scroll member 9 so that both the scroll members 7 and 9 synchronously revolve.
  • a driven side support member 22 is fixed to the distal end (free end) of the driven side wall body 9b of the driven side scroll member 9 via a pin 24b.
  • a driving side scroll member 7 is sandwiched between the driven side support member 22 and the driven side scroll member 9. Therefore, the driving side end plate 7a is arranged to face the driven side support member 22.
  • the driven side support member 22 has a driven side support member shaft part 22a on the center side, which is rotatably attached to the housing 3 via a driven side support member bearing 28 which is the angular ball bearing. As a result, the driven side support member 22 rotates around the driven side rotation axis CL2 like the driven side scroll member 9.
  • a pin ring mechanism 15 is provided between the driven side support member 22 and the driving side end plate 7a.
  • the pin ring mechanism 15 is used as the synchronous driving mechanism transmitting the driving force from the driving side scroll member 7 to the driven side scroll member 9 so that both the scroll members 7 and 9 synchronously revolve.
  • Fig. 7 the preload directions of each of the bearings 11, 13, 26 and 28 are shown.
  • the preload direction contact angle caused by a preload
  • the preload direction is indicated by black thick solid lines on the bearings 11, 13, 26 and 28.
  • a preload is applied to the driven side shaft part 9c by the preload member 14a so that the clearance on the inner ring side of the driven side support member bearing 28 side (right side in Fig. 7 ) becomes zero. That is, the right side face of the inner ring of the driven side bearing 13 contacts against the left side face of the enlarged diameter part of the driven side shaft part 9c.
  • a preload is applied to the driven side support member shaft part 22a so that the clearance on the inner ring side on the driven side bearing 13 side (left side in Fig. 7 ) becomes zero. That is, the left side face of the inner ring of the driven side support member bearing 28 contacts against the right side face of the enlarged diameter part of the driven side support member shaft part 22a.
  • the driven side bearing 13 and the driven side support member bearing 28 are in a DB (back surface combination) preloading relation.
  • DB back surface combination
  • the application of the DB preload allows the deformation in the direction in which the distance between the inner ring of the driven side bearing 13 and the inner ring of the driven side support member bearing 28 increases, according to the axial deformation of the driven side scroll member 9.
  • a preload is applied to the driving side shaft part 7c so that the inner ring is urged in the direction of the driving side support member bearing 26 (left direction in Fig. 7 ).
  • a preload is applied to the driving side support member shaft part 20a so that the inner ring is urged in the outward direction of the housing 3 (left direction in Fig. 7 ).
  • a preload is applied to the driving side bearing 11 and the driving side support member bearing 26 when the motor housing part 3a and the scroll housing part 3b of the housing 3 are assembled by the bolts 32. That is, a preload is applied when the motor housing part 3a and the scroll housing part 3b are contacted each other in the axial direction and tightened by the bolts 32.
  • the co-rotating scroll compressor 1B having the above configuration operates as follows.
  • the rotation of the drive shaft around the driving side rotation axis CL1 by the motor also rotates the driving side shaft part 7c connected to the drive shaft so that the driving side scroll member 7 rotates around the driving side rotation axis CL1.
  • the rotation of the driving side scroll member 7 transmits the driving force from the driving side end plate 7a to the driven side support member 22 via the pin ring mechanism 15.
  • the driving force is transmitted from the driving side support member 20 to the driven side end plate 9a via the pin ring mechanism 15.
  • the driving force is transmitted to the driven side scroll member 9, and the driven side scroll member 9 rotates around the driven side rotation axis CL2.
  • the movement of the pin member 15b of the pin ring mechanism 15 in contact with the ring member 15a causes both the scroll members 7 and 9 to relatively revolve.
  • both the scroll members 7 and 9 causes the air sucked from the suction port of the housing 3 to be sucked from the outer peripheral sides of both the scroll members 7 and 9, and taken into the compression chambers formed by both the scroll members 7 and 9.
  • the volume decreases, and accordingly the air is compressed.
  • the compressed air in this way passes through the discharge port 9d of the driven side scroll member 9, and is discharged to the outside from the discharge port 3d of the housing 3.
  • the discharged compressed air is guided to an internal combustion engine which is not shown and used as combustion air.
  • the driven side bearing 13 and the driven side support member bearing 28 rotatably support each of the shaft parts 9c and 22a.
  • the rotation of the driven side scroll member 9 generates the centrifugal force to deform the driven side wall bodies 9b of the driven side scroll member 9 radially outward (see, for example, the deformation shown in Fig. 5 ) .
  • the radially outward deformation of the outer peripheral side of the driven side scroll member 9 tends to cause the driven side scroll member 9 to deform to decrease a distance to axial direction between the shaft part 9c supported by the driven side bearing 13 and the shaft part 22a supported by the driven side support member bearing 28 (see the broken line shown in Fig. 5(a) , for example).
  • Such allowance of the deformation further increases the deformation radially outward on the outer peripheral side of the driven side scroll member 9.
  • a preload is applied to the driven side shaft part 9c so that an axial clearance in the driven side support member bearing 28 direction is eliminated in the driven side bearing 13 and a preload is applied to the driven side support member shaft part 22a so that an axial clearance in the driven side bearing 13 direction is eliminated in the driven side support member bearing 28.
  • the increase of temperature during the operation in the co-rotating scroll compressor 1B tends to cause the driven side scroll member 9 to thermally expand, and deform to increase a distance to axial direction between both the shaft parts 9c and 22a supported by each of the bearings 13 and 28.
  • the restraint of the deformation leads to the increase in the thermal stress generated in the driven side scroll member 9 as shown in Fig. 6(a) , for example.
  • the distal ends of the driven side wall body 9b and the driven side support member 22 are fixed by the pin 24b to allow the displacement in the axial direction, and both the shaft parts 9c and 22a are supported by each of the bearings 13 and 28 to allow the increase in the distance between both the shaft parts 9c and 22a supported by each of the bearings 13 and 28, that is, to allow the increase in the distance between the inner ring of the driven side bearing 13 and the inner ring of the driven side support member bearing 28.
  • the distance between both the shaft parts 9c and 22a supported by each of the bearings 13 and 28 can be increased according to the thermal expansion, so that the generation of the thermal stress can be suppressed.
  • the preload directions of the driving side bearing 11 and the driven side support member bearing 26 may be set.
  • Fig. 8 to Fig. 23 there is shown a modification of how a preload is applied to the bearings of the co-rotating scroll compressor 1A shown in the first embodiment described above, that is, the modification of how a preload is applied to the both co-rotating scroll compressor of double-teeth with two wall bodies of 71b, 72b, 91b and 92b provided for each of the driving side scroll member 70 and the driven side scroll member 90. Therefore, the same reference numerals are given to the same configurations as those of the co-rotating scroll compressor 1A of the first embodiment, and the description thereof is omitted.
  • Fig. 8 shows a modification of how a preload is applied to the drive shaft 6 side, for the first embodiment.
  • an inner ring is loosely fitted to be fixed to be movable in the axial direction with respect to the second driving side shaft part 72c, and the outer ring is tightly fitted to be fixed not to move in the axial direction with respect to the housing 3.
  • an inner ring is loosely fitted to be fixed to be movable in the axial direction with respect to the first drive shaft part 7c and the outer ring is tightly fitted to be fixed not to move in the axial direction with respect to the housing 3.
  • the inner ring is loosely fitted to be fixed to be movable in the axial direction with respect to the drive shaft 6, and the outer ring is tightly fitted to be fixed not to move in the axial direction with respect to the housing 3.
  • a preload member 17a pressing the inner ring of the rear end bearing 17 toward the driving side scroll member 70 side is provided.
  • the preload member 17a is a nut or the like, and is screwed to the drive shaft 6. The application of a preload to the inner ring of the rear end bearing 17 by the preload member 17a causes a load to be applied from the right side of the inner ring to the left side of the outer ring, as shown by the thick solid line in the figure.
  • the preload direction of the second driving side bearing 14 is the direction from the right side of the inner ring to the left side of the outer ring and the preload direction of the first driving side bearing 11 is the direction from the left side of the inner ring to the right side of the outer ring.
  • a preload is applied to the second driving side bearing 14 and the first driving side bearing 12 when the motor housing part 3a and the scroll housing part 3b of the housing 3 are contacted to be fixed by the bolts 32 in the axial direction.
  • the preload member is provided only on the rear end bearing 17, and it is not necessary to provide the preload member on the first driving side bearing 11 and the second driving side bearing 14, so that the number of parts can be reduced.
  • Fig. 11 shows a combination of fitting of each bearing 11, 14 and 17 and presence or absence of the preload member.
  • the configuration described above is referred to as Modification 1-1.
  • the fitting between the second driving side bearing 14 and the first driving side bearing 11 may be a movable loose in the axial direction for both the inner ring and the outer ring. Thereby, the attachment of the bearings 14 and 11 is facilitated and the assembling property improved.
  • the inner ring of the second driving side bearing 14 is set to loose and the outer ring of the second driving side bearing 14 is set to tight, and the inner ring and the outer ring of the first driving side bearing 11 are set to tight. In this way, making the inner ring of the first driving side bearing 11 tight also reduces the misalignment amount around the driving side rotation axis CL1.
  • the first driving side bearing 11 is attached to the same motor housing part 3a as the motor 5, so that it is possible to reliably determine the positional relation with the motor 5.
  • the preload member 14a pressing the inner ring of the second driving side bearing 14 toward the left side (side opposite to the motor 5) may be provided.
  • the preload direction of the rear end bearing 17 is different from that in Modification 1 described above, and the other preload directions are the same.
  • the preload member 17a pressing the inner ring of the rear end bearing 17 toward the right side is provided on the left side of the rear end bearing 17, the preload member 17a pressing the inner ring of the rear end bearing 17 toward the right side (in the direction opposite to the driving side scroll member 70 side) is provided.
  • the application of a preload to the inner ring of the rear end bearing 17 by the preload member 17a causes the load to be applied from the left side of the inner ring to the right side of the outer ring, as shown by the thick solid line in the figure.
  • the preload member 11a pressing the inner ring of the first driving side bearing 11 toward the right side (the rear end bearing 17 side) is provided.
  • Fig. 13 shows a combination of fitting of each of the bearings 11, 14 and 17 and presence or absence of the preload member.
  • the preload member 14a pressing the inner ring of the second driving side bearing 14 toward the left side may be provided as shown in Fig. 10 .
  • the preload directions of the first driving side bearing 11 and the second driving side bearing 14 are different from those of Modification 1 described above, and the preload direction of the rear end bearing 17 is the same.
  • the preload members 11a, 14a and 17a are provided for each of the bearings 11, 14, and 17.
  • the preload member 14a pressing the inner ring of the second driving side bearing 14 to the right side (direction toward the driving side scroll member 70 side) is provided.
  • the application of a preload to the inner ring of the second driving side bearing 14 by the preload member 14a causes the load to be applied from the left side of the inner ring toward the right side of the outer ring, as shown by the thick solid line in the figure.
  • the preload member 11a pressing the inner ring of the first driving side bearing 11 toward the left side (the direction toward the driving side scroll member 70 side) is provided.
  • the application of a preload to the inner ring of the first driving side bearing 11 by the preload member 11a causes the load to be applied from the right side of the inner ring to the left side of the outer ring, as shown by the thick solid line in the figure.
  • the preload member 17a pressing the inner ring of the rear end bearing 17 toward the left side is provided on the right side of the rear end bearing 17, the preload member 17a pressing the inner ring of the rear end bearing 17 toward the left side (direction toward the driving side scroll member 70 side) is provided.
  • the application of a preload to the inner ring of the rear end bearing 17 by the preload member 17a causes the load to be applied from the right side of the inner ring to the left side of the outer ring, as shown by the thick solid line in the figure.
  • Fig. 15 shows a combination of fitting of each of the bearings 11, 14 and 17 and presence or absence of the preload member.
  • the preload direction of the rear end bearing 17 is different from that of Modification 3 described above, and the other preload directions are the same.
  • Fig. 17 shows a combination of fitting of each of the bearings 11, 14 and 17 and presence or absence of the preload member.
  • Fig. 18 shows a modification of how a preload is applied to the support member bearings 37 and 38 on the driven side, for the first embodiment.
  • the inner ring is loosely fitted to be fixed to be movable in the axial direction with respect to the second support member shaft part 35a, and the outer ring is tightly fitted to be fixed not to move in the axial direction with respect to the housing 3.
  • a preload member 38a pressing the inner ring of the second support member bearing 38 toward the driven side scroll member 90 side is provided.
  • the preload member 38a is a nut or the like, and is screwed to the second support member shaft part 35a.
  • the application of a preload to the inner ring of the second support member bearing 38 by the preload member 38a causes the load to be applied from the left side of the inner ring to the right side of the outer ring, as shown by the thick solid line in the figure.
  • the inner ring is loosely fitted to be fixed to be movable in the axial direction with respect to the first support member shaft part 33a, and the outer ring is tightly fitted to be fixed not to move in the axial direction with respect to the housing 3.
  • the preload member 37a pressing the inner ring of the first support member bearing 37 toward the driven side scroll member 90 side is provided.
  • the preload member 37a is a nut or the like, and is screwed to the first support member shaft part 33a.
  • the application of a preload to the inner ring of the first support member bearing 37 by the preload member 37a causes the load to be applied from the right side of the inner ring to the left side of the outer ring, as shown by the thick solid line in the figure.
  • the suppression of the deformation in which a distance to axial direction between both the shaft parts 33a and 35a supported by each of the bearings 37 and 38 decreases can alleviate the stress generated in the driven side scroll member 90, further suppress the leakage of the compressed air generated by the deformation of the driven side scroll member 90.
  • the distance between both the shaft parts 33a and 35a supported by each of the bearings 37 and 38 can be increased according to the thermal expansion, so that the generation of the thermal stress can be suppressed.
  • Fig. 19 a combination of fitting of each of the bearings 37 and 38 and presence or absence of the preload member is shown.
  • the above-described configuration is Modification 5-1.
  • Modification 5-2 the inner ring of the second support member bearing 38 is set to tight with respect to Modification 5-1. Thereby, it is possible to reduce the misalignment amount around the driven side rotation axis CL2. In this case, the preload member 38a of the second support member bearing 38 can be omitted, and the number of parts can be reduced.
  • the inner ring of the first support member bearing 37 is set to tight with respect to Modification 5-1. Thereby, it is possible to reduce the misalignment amount around the driven side rotation axis CL2. In this case, a preload member 37a of the first support member bearing 37 can be omitted, and the number of parts can be reduced.
  • the preload member 38a pressing the inner ring of the second support member bearing 38 toward the left side (opposite direction to the driven side scroll member 90 side) is provided.
  • the application of a preload to the inner ring of the second support member bearing 38 by the preload member 38a causes the load to be applied from the right side of the inner ring to the left side of the outer ring, as shown by the thick solid line in the figure.
  • the preload member 37a pressing the inner ring of the first support member bearing 37 toward the right side (opposite direction to the driven side scroll member 90 side) is provided.
  • the application of a preload to the inner ring of the first support member bearing 37 by the preload member 37a causes the load to be applied from the left side of the inner ring to the right side of the outer ring, as shown by the thick solid line in the figure.
  • a preload is applied to each of the bearing 37 and 38 when the motor housing part 3a and the scroll housing part 3b of the housing 3 are contacted to be fixed by the bolts 32 in the axial direction, it is possible to omit the preload members 37a and 38a.
  • Fig. 21 the fitting combination of each of the bearings 37 and 38 is shown.
  • the preload members 37a and 38a can be omitted if a preload is applied when the motor housing part 3a and the scroll housing part 3b of the housing 3 are contacted to be fixed by the bolts 32 in the axial direction.
  • Modification 6-3 the inner ring of the second support member bearing 38 is set to tight with respect to Modification 6-1. Thereby, it is possible to reduce the misalignment amount around the driven side rotation axis CL2.
  • Modification 7 is different from the above Modification 5 in that the preload members 37a and 38a are omitted, and the preload direction is the same.
  • this modification is different from Modification 5 in that the shaft part 33a of the first support member 33 is fitted to the outer ring of the first support member bearing 37, and the housing 3 is fitted to the inner ring of the first support member bearing 37.
  • this modification is different from Modification 5 in that the shaft part 35a of the second support member 35 is fitted to the outer ring of the second support member bearing 38, and the inner ring of the second support member bearing 38 is fitted to the housing 3 .
  • a preload is applied to each of the bearing 37 and 38 when the motor housing part 3a and the scroll housing part 3b of the housing 3 are contacted to be fixed by the bolts 32 in the axial direction.
  • Modification 7-3 the inner ring of the second support member bearing 38 is set to tight with respect to Modification 7-1. Thereby, it is possible to reduce the misalignment amount around the driven side rotation axis CL2.
  • Modification 7-4 the inner ring of the first support member bearing 37 is set to tight with respect to Modification 7-1. Thereby, it is possible to reduce the misalignment amount around the driven side rotation axis CL2.
  • the first driving side bearing 11 may be omitted, and the second driving side bearing 14 and the rear end bearing 17 may support the rotation around the driving side rotation axis CL1. As a result, the number of parts can be reduced.
  • a preload as shown in Fig. 24 , applying a preload by the rear end bearing 17 instead of the first driving side bearing 11 can obtain the same effect as in the first embodiment.
  • the co-rotating scroll compressor is used as a supercharger, but the present invention is not limited to this, and it can be widely used as long as it compresses a fluid, and it can also be used as a refrigerant compressor used in, for example, an air conditioner.
EP17841518.8A 2016-08-19 2017-08-15 Bidirectional-rotation-type scroll compressor Active EP3489514B1 (en)

Applications Claiming Priority (2)

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JP2016161317A JP6768406B2 (ja) 2016-08-19 2016-08-19 両回転スクロール型圧縮機
PCT/JP2017/029415 WO2018034296A1 (ja) 2016-08-19 2017-08-15 両回転スクロール型圧縮機

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JP6749829B2 (ja) * 2016-11-24 2020-09-02 三菱重工業株式会社 両回転スクロール型圧縮機
US11111921B2 (en) 2017-02-06 2021-09-07 Emerson Climate Technologies, Inc. Co-rotating compressor
JP6698726B2 (ja) * 2018-03-12 2020-05-27 三菱重工業株式会社 両回転スクロール型圧縮機
EP4058675A4 (en) 2019-11-15 2023-11-29 Emerson Climate Technologies, Inc. CO-ROTATING SPIRAL COMPRESSOR
US11732713B2 (en) 2021-11-05 2023-08-22 Emerson Climate Technologies, Inc. Co-rotating scroll compressor having synchronization mechanism
US11624366B1 (en) 2021-11-05 2023-04-11 Emerson Climate Technologies, Inc. Co-rotating scroll compressor having first and second Oldham couplings

Family Cites Families (5)

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Publication number Priority date Publication date Assignee Title
DE3402548A1 (de) * 1984-01-26 1985-08-01 Leybold-Heraeus GmbH, 5000 Köln Verdraengermaschine
JP5076242B2 (ja) * 2007-03-30 2012-11-21 アネスト岩田株式会社 スクロール式流体機械
JP2012215092A (ja) * 2011-03-31 2012-11-08 Toyota Industries Corp 両回転スクロール型圧縮機
JP5578159B2 (ja) * 2011-11-18 2014-08-27 株式会社豊田自動織機 車両用圧縮機
JP6161407B2 (ja) * 2013-05-28 2017-07-12 有限会社スクロール技研 スクロール流体機械

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
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JP2018028307A (ja) 2018-02-22
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CN109642571A (zh) 2019-04-16
WO2018034296A1 (ja) 2018-02-22
US20190178247A1 (en) 2019-06-13
JP6768406B2 (ja) 2020-10-14

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