Patent Application
20190178247
The present invention relates to a co-rotating scroll compressor.
Conventionally, 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.
[PTL 1] the Publication of Japanese Patent No. 5443132
In the co-rotating scroll compressor as in PTL 1, deformation is generated by a centrifugal force in a scroll part. In particular, in the case of high-speed rotation, the deformation caused by the centrifugal force can not be ignored.
In addition, when a temperature rises during the operation of the co-rotating scroll compressor, 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.
To solve the above problem, a co-rotating scroll compressor of the present invention employs the following solutions.
The co-rotating scroll compressor according to the present invention 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 scroll member, a preload is applied to the shaft part so that an axial clearance in a second driving side bearing direction is eliminated in the first driving side bearing, and a preload is applied to the shaft part so that an axial clearance in a first driving side bearing direction is eliminated in the second driving side bearing, and/or a preload is applied to the shaft part so that an axial clearance in a 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 a first driven side bearing direction is eliminated in the second driven side bearing.
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. Thereby, 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. As a result, 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. In this way, the co-rotating scroll compressor is provided in which both the driving side scroll member and the driven side scroll member rotate.
In the driving side scroll member, 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. As described above, 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. Therefore, 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, and 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. Thereby, suppression of the deformation in which the distance to axial direction between both the shaft parts supported by each of the driving side bearings decreases, can alleviate stress generated in the driving side scroll member, further suppress leakage of compressed fluid generated by the deformation of the driving side scroll member.
Similarly, in the driven side scroll member, 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. As described above, 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. Therefore, 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. Thereby, the suppression of the deformation in which the distance to axial direction between both the shaft parts supported by each of the driven side bearings decreases, can alleviate the stress generated in the driven side scroll member, further suppress the leakage of compressed fluid generated by the deformation of the driven side scroll member.
Further, 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 bearing 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.
Further, in the co-rotating scroll compressor according to the present invention, 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, and 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, and/or 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, 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 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. As a result, 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.
For example, 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. Further, for example, 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.
Similarly for the driven side, 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. As a result, 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.
For example, 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. Further, for example, 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.
Further, the co-rotating scroll compressor provided with, 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 member 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 side in the axial direction of the second driven side wall body and rotating together with the second driven side wall body, wherein the first driving side bearing supports a shaft part of the first driving side scroll part, the second driving side bearing supports a shaft part of the second driving side scroll part, the first driven side bearing supports a bearing of the first support member, and the second driven side bearing supports a shaft part of the second support member.
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.
Further, in co-rotating scroll compressor, the fixed portion of wall is fixed to allow the displacement in the axial direction, and 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, and/or 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, and 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. As a result, 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.
For example, as for the fixed portion of wall, a pin is used to allow the displacement in the axial direction. Further, for example, 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.
Similarly for the driven side, 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. As a result, 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.
For example, the distal end of 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. Further, for example, 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.
Further, 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.
Contacting the first housing and the second housing each other in the axial direction to be fixed applies a preload to the bearings, so that it is unnecessary to provide a preload member (such as a nut) for applying a preload. As a result, the number of parts can be reduced, and assembling property is improved.
Further, in the co-rotating scroll compressor according to the present invention, 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. Thereby, it is not necessary to provide the driving side shaft part between the driving side end plate and the drive part, and the number of parts can be reduced. Even if the driving side shaft part is provided between the driving side end plate and the drive part, applying a preload by the first driving side bearing provided on the opposite side of the drive part can reduce a burden on the driving side shaft part provided between the driving side end plate and the drive part.
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 a change 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.
Hereinafter, a first embodiment of the present invention will be described with reference to
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. Although not shown in
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. As shown in
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.
At the rear end (right end in
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
As shown in
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. On the side of the inner ring of the second driving side bearing 14, a preload member 14a such as a nut, a disk spring is provided. 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. As a result, 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
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.
On both sides of the driven side end plate 90a, 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, and 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.
As shown in
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, and 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
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. 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. As a result, the driven side scroll member 90 rotates around the driven side rotation axis CL2 via each of the support members 33 and 35.
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.
In
In the second driving side bearing 14, 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
In the first driving side bearing 11, 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
Therefore, the first driving side bearing 11 and the second driving side bearing 14 are in a DB (back surface combination) preloading relation. As described above, 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.
Further, as described above, 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
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. At this time, 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.
The revolving motion of 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.
According to the present embodiment, the following operational effects are obtained.
In the driving side scroll member 70, 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
Therefore, in the present embodiment, 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. Thereby, as shown in
An increase of temperature during the operation in the co-rotating scroll compressor 1A tends to cause the driving side scroll member 70 to thermally expand, and deform to increase a distance to axial direction between both the shaft parts 7c and 72c supported by each of the driving side bearings 11 and 14. The restraint of the deformation leads to the increase in the thermal stress generated in the driving side scroll member 70 as shown in
Therefore, 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. As a result, as shown in
Contacting the motor housing part 3a and the scroll housing part 3b of the housing 3 each other in the axial direction to be fixed by the bolts 32 applies a preload to the first support member bearing 37 and the second support member bearing 38, so that it is unnecessary to provide the preload member for applying a preload. As a result, the number of parts can be reduced, and assembling property is improved.
As for the driven side scroll member 90, similarly to the driving side scroll member 70, in order to alleviate the deformation caused by the centrifugal force and the thermal stress, the preload directions of the first support member bearing 37 and the second support member bearing 38 may be set.
Next, a second embodiment of the present invention will be described with reference to
In the first embodiment described above, 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. Like the first driving side wall body 71b shown in
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
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.
In
In the driven side bearing 13, 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
In the driven side support member bearing 28, 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
Therefore, the driven side bearing 13 and the driven side support member bearing 28 are in a DB (back surface combination) preloading relation. As described above, the restraint in the axial direction of the driven side scroll member 9 by each of the inner rings of the driven side bearing 13 and the driven side support member bearing 28 suppresses the deformation in the direction in which the driven side shaft part 9c of the driven side scroll member 9 and the driven side support member shaft part 22a approaches each other.
Further, as described above, 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.
In the driving side bearing 11, 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
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. In addition, 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. As a result, 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. At this time, 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.
The revolving motion of 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. As the taken air moves toward the center side in the compression chamber, 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 operational effects according to the present embodiment are as follows.
In the driven side scroll member 9 and the driven side scroll support member 22, 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
Therefore, in the present embodiment, 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. Thereby, for example, similarly to the deformation shown in
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
Therefore, 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. As a result, for example, similarly to the deformation shown in
Contacting the motor housing part 3a and the scroll housing part 3b of the housing 3 each other in the axial direction to be fixed by the bolts 32 applies a preload to the driving side bearing 11 and the driving side support member bearing 26, so that it is unnecessary to provide the preload member for applying a preload. As a result, the number of parts can be reduced, and assembling property is improved.
As for the driving side scroll member 7, similarly to the driven side scroll member 9, in order to alleviate the deformation caused by the centrifugal force and the thermal stress, the preload directions of the driving side bearing 11 and the driven side support member bearing 26 may be set.
In
In the second driving side bearing 14, an inner ring is loosely fitted to be fixed to be movable in the axial direction with respect to the second drive 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.
In the first driving side bearing 11, 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.
In the rear end bearing 17 provided at the rear end (the right end in
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.
According to such a configuration, 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.
As shown in Modification 1-2, 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.
In Modification 1-3, 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. In addition, 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.
In Modification 1-4, instead of tightening the inner ring of the first driving side bearing 11 as in Modification 1-3, the inner ring of the rear end bearing 17 is set to tight. Even with such a configuration, it is possible to reduce the misalignment amount around the driving side rotation axis CL1. In this case, as shown in
Further, as shown in
As shown in
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.
In addition, 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.
In Modification 2-1, the inner rings of each of the bearings 11, 14 and 17 are set to loose and the outer ring is set to tight. And fixing the preload members 11a and 17a and the housing 3 causes a preload to be applied to each of the bearings 11, 14 and 17.
In Modification 2-2, setting the inner ring of the second driving side bearing 14 to tight reduces the misalignment amount around the driving side rotation axis CL1.
In Modification 2-3, setting the inner ring of the first driving side bearing 11 to tight reduces the misalignment amount around the driving side rotation axis CL1.
In Modification 2-4, setting all the inner rings and outer rings of each of the bearings 11, 14 and 17 to loose facilitates the attachment of each of the bearings 11, 14, and 17, thereby improving assembling property.
For each of Modifications 2-1 to 2-4, 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 as shown in
As shown in
In Modification 3-1, the preload members 11a, 14a and 17a are provided for each of the bearings 11, 14, and 17.
On the left side of the second driving side bearing 14, 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.
On the right side of the first driving side bearing 11, 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.
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.
In Modification 3-2, the preload member 14a of the second driving side bearing 14 of Modification 3-1 described above is omitted, and the inner ring of the second driving side bearing 14 is set to tight. As a result, the number of parts is reduced, and the misalignment amount around the driving side rotation axis CL1 is reduced.
In Modification 3-3, the preload member 11a of the first driving side bearing 11 of Modification 3-1 described above is omitted, and the inner ring of the first driving side bearing 11 is set to tight. As a result, the number of parts is reduced, and the misalignment amount around the driving side rotation axis CL1 is reduced.
In Modification 3-4, the preload member 17a of the rear end bearing 17 of Modification 3-1 described above is omitted, and the inner ring of the rear end bearing 17 is set to tight. As a result, the number of parts is reduced, and the misalignment amount around the driving side rotation axis CL1 is reduced.
As shown in
In Modification 4-1, 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.
In Modification 4-2, the preload member 14a of the second driving side bearing 14 of Modification 4-1 described above is omitted, and the inner ring of the second driving side bearing 14 is set to tight. As a result, the number of parts is reduced, and the misalignment amount around the driving side rotation axis CL1 is reduced.
In Modification 4-3, the preload member 11a of the first driving side bearing 11 of Modification 4-1 described above is omitted, and the inner ring of the first driving side bearing 11 is set to tight. As a result, the number of parts is reduced, and the misalignment amount around the driving side rotation axis CL1 is reduced.
In Modification 4-4, the preload member 17a of the rear end bearing 17 of Modification 4-1 described above is omitted, and the inner ring of the rear end bearing 17 is set to tight. As a result, the number of parts is reduced, and the misalignment amount around the driving side rotation axis CL1 is reduced.
In the second support member bearing 38, 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. On the left side of the second support member bearing 38, 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.
In the first support member bearing 37, 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. On the right side of the first support member bearing 37, 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.
According to such a configuration, similarly to the deformation shown in
Further, for example, similarly to the deformation shown in
In
In 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.
In Modification 5-3, 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.
As shown in
On the right side of the second support member bearing 38, 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.
On the left side of the first support member bearing 37, 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.
In
In Modification 6-1, the inner ring of each of the bearings 37 and 38 is set to be loose and the outer ring is set to tight.
In Modification 6-2, the outer rings of both the bearings 37 and 38 are set to loose with respect to Modification 6-1. Thereby, the attachment of each of the bearings 37 and 38 is facilitated and the assembling property improved.
In 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.
In Modification 6-4, the inner ring of the first support member bearing 37 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.
As shown in
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.
In
In Modification 7-1, the inner ring of each of the bearings 37 and 38 is set to loose and the outer ring is set to tight.
In Modification 7-2, the outer rings of both the bearings 37 and 38 are set to loose with respect to Modification 7-1. Thereby, the attachment of each of the bearings 37 and 38 is facilitated and the assembling property is improved.
In 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.
In 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.
As shown in
In each of the above-described embodiments and modifications, 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.
| Number | Date | Country | Kind |
|---|---|---|---|
| 2016-161317 | Aug 2016 | JP | national |
| Filing Document | Filing Date | Country | Kind |
|---|---|---|---|
| PCT/JP2017/029415 | 8/15/2017 | WO | 00 |
