JP2019183832A - Scroll type compressor - Google Patents

Abstract

To provide a scroll type compressor capable of suppressing vibration of a rotating shaft in accompany with swing of a balancer, and reducing a load applied to a bearing for the rotating shaft.SOLUTION: A scroll type compressor includes a balancer 40 rotated integrally with a rotating shaft 14. A bush 36 includes a cylindrical portion 37 externally fitted to an inner peripheral face of a bearing for a scroll, and provided with an insertion hole 36a in an axial direction, and an auxiliary weight portion 43 disposed at a radial outer side with respect to the cylindrical portion 37. A position of the insertion hole 36a is determined on a position where moment Ma around an eccentric shaft 35 generated by centrifugal force Fa acting on a movable scroll 32 and moment Mb around the eccentric shaft 35 generated by centrifugal force Fb acting on the auxiliary weight portion 43 are directed in opposite directions. A center of gravity Z of the bush 36 is positioned at a side same as a center axis M of the eccentric shaft 35 with respect to a straight line T connecting a central axis N of the cylindrical portion 37 and a central axis L of the rotating shaft 14 when observed from the axial direction of the rotating shaft 14.SELECTED DRAWING: Figure 3

Description

  The present invention relates to a scroll compressor having a bush into which an eccentric shaft is inserted and a balancer that rotates integrally with a rotary shaft.

  In the scroll compressor, in order to keep the contact pressure between the spiral wall of the movable scroll and the spiral wall of the fixed scroll appropriately, a mechanism that makes the revolution radius of the movable scroll variable is adopted. As such a mechanism, a structure in which a bush is provided between an eccentric shaft of a rotating shaft and a movable scroll is known. An eccentric shaft provided on one end surface of the rotating shaft is fitted into the bush. A movable scroll is supported on the bush via a bearing. When the rotating shaft rotates, the movable scroll revolves around the eccentric shaft. At this time, the revolution radius of the movable scroll is changed by the swing of the bush within the specified range.

  However, a moment is generated around the eccentric shaft of the bush in response to the centrifugal force generated with the revolving motion of the movable scroll. Then, a load is applied to the bearing that supports the rotating shaft. In order to reduce the load applied to the bearing that supports the rotating shaft, for example, as disclosed in Patent Document 1, a structure in which a balancer is integrated with a bush has been proposed. When the rotating shaft rotates, the balancer-integrated bush revolves.However, when the balancer swings due to centrifugal force, the moment due to the centrifugal force of the balancer is different from the moment due to the centrifugal force of the movable scroll. Occurs in the opposite direction. Then, the moment is canceled and the load applied to the rotary shaft bearing that supports the rotary shaft can be reduced.

  However, in the balancer-integrated bush, when the bush swings, the balancer also swings simultaneously. Since the balancer is heavier than the bush, the vibration of the rotating shaft is likely to deteriorate due to the swing of the balancer. Thus, a scroll compressor has been proposed in which a balancer and a bush are separated (see, for example, Patent Document 2). In Patent Document 2, the balancer is fixed to the rotating shaft and rotates integrally with the rotating shaft. For this reason, since the swing of the balancer is eliminated, the deterioration of the vibration of the rotating shaft is suppressed.

JP 2014-173436 A Japanese Patent Laying-Open No. 2015-68248

  However, in the scroll compressor disclosed in Patent Document 2, since the balancer is separated from the bush, the moment due to the centrifugal force acting on the movable scroll cannot be offset by the balancer, and the rotary shaft bearing supports the rotary shaft. The load applied to can not be reduced. As a result, it is necessary to increase the size of the rotary shaft bearing to withstand the load applied to the rotary shaft bearing.

  An object of the present invention is to provide a scroll type compressor that can suppress vibration of a rotating shaft accompanying a swing of a balancer and reduce a load applied to a rotating shaft bearing.

  A scroll type compressor for solving the above-mentioned problems has a rotating shaft, an eccentric shaft provided at a tip of the rotating shaft, a fixed side substrate, and a fixed side spiral wall standing up from the fixed side substrate. A fixed scroll, a disk-shaped movable side substrate facing the fixed side substrate, a movable side spiral wall standing from the movable side substrate toward the fixed side substrate and meshing with the fixed side spiral wall; and A movable scroll that rises from the movable substrate toward the rotation axis and has a cylindrical boss formed around a central axis of the movable substrate, and compresses fluid by rotation of the rotation shaft, and the rotation A bushing having an insertion hole into which the shaft is inserted, a shaft support member provided with a bearing for a rotating shaft for supporting the rotating shaft in the insertion hole, and an insertion hole into which the eccentric shaft is inserted And the inner circumference of the boss A scroll type compressor having a scroll bearing fitted on the outer peripheral surface of the bush and having a central axis of the movable side substrate and a central axis of the eccentric shaft different from each other, The balancer includes a balancer that rotates integrally with the rotary shaft and has a main weight portion located on the opposite side of the eccentric shaft across the central axis of the rotary shaft, and the bush is fitted on the inner peripheral surface of the scroll bearing. And a cylindrical portion in which the insertion hole is formed in the axial direction, and a sub-weight portion disposed radially outward from the cylindrical portion, and the insertion hole is accompanied by rotation of the rotating shaft. The moment about the eccentric shaft generated by the centrifugal force acting on the movable scroll and the moment about the eccentric shaft generated by the centrifugal force acting on the sub-weight portion with the rotation of the rotating shaft are: Each of the bushes is provided at a position opposite to each other, and when viewed from the axial direction of the rotary shaft, the center of gravity of the bush is in relation to the straight line connecting the center of the cylindrical portion and the center of the rotary shaft. The gist is that it is located on the same side as the center.

  According to this, it is possible to balance the weight with the movable scroll by the main weight portion of the balancer integrated with the rotating shaft. Since the balancer is separated from the bush, the balancer does not swing at the same time as the bush, and the vibration of the rotating shaft accompanying the swing of the balancer can be suppressed. Then, the position of the insertion hole was adjusted so that the moment generated by the centrifugal force acting on the movable scroll and the moment generated by the centrifugal force acting on the subweight portion were in opposite directions. By adjusting the position of the insertion hole, the moment around the eccentric shaft can be offset, and the load applied to the rotary shaft bearing that supports the rotary shaft can be reduced. As a result, the rotary shaft bearing can be downsized.

  Furthermore, the eccentric shaft generated by the centrifugal force acting on the sub-weight portion by positioning the center of gravity of the bush on the same side as the center of the eccentric shaft with respect to the straight line connecting the center of the cylindrical portion and the center of the rotating shaft The turning moment can be increased. As a result, the subweight portion can be reduced in size.

  Further, regarding the scroll compressor, the center of gravity of the sub-weight portion when viewed from the axial direction of the rotating shaft is the center of the eccentric shaft with respect to a straight line connecting the center of the cylindrical portion and the center of the rotating shaft. It should be located on the same side. As a result, the moment about the eccentric shaft generated by the centrifugal force acting on the subweight portion can be further increased, and as a result, the subweight portion can be reduced in size.

  Further, in the scroll compressor, as viewed from the axial direction of the rotary shaft, the whole of the sub-weight portion has a center of the eccentric shaft with respect to a straight line connecting the center of the cylindrical portion and the center of the rotary shaft. It should be located on the same side. As a result, the moment around the eccentric shaft generated by the centrifugal force acting on the subweight portion can be further increased, and as a result, the subweight portion can be reduced in size.

  Further, in the scroll compressor, the sub-weight portion is provided along the radial direction of the cylindrical portion, from a thin portion extending from the outer peripheral surface of the cylindrical portion, to the radially outer side than the thin portion, and A thick portion having a dimension along the axial direction of the rotating shaft that is larger than the thin portion, and when viewed from the axial direction of the rotating shaft, the entire thick portion is formed between the center of the cylindrical portion and the rotating shaft. It may be located on the same side as the center of the eccentric shaft with respect to the straight line connecting the centers.

  According to this, even if the position of the bush with respect to the rotating shaft slightly varies due to the manufacturing tolerance of the bush or the assembly tolerance of the bush and the rotating shaft, the center of gravity of the bush and the center of the rotating shaft Can be located on the same side as the center of the eccentric shaft. Further, this makes it possible to further increase the moment around the eccentric shaft generated by the centrifugal force acting on the subweight portion, and as a result, the subweight portion can be reduced in size.

  A scroll type compressor for solving the above-mentioned problems has a rotating shaft, an eccentric shaft provided at a tip of the rotating shaft, a fixed side substrate, and a fixed side spiral wall standing up from the fixed side substrate. A fixed scroll, a disk-shaped movable side substrate facing the fixed side substrate, a movable side spiral wall standing from the movable side substrate toward the fixed side substrate and meshing with the fixed side spiral wall; and A movable scroll that rises from the movable substrate toward the rotation axis and has a cylindrical boss formed around a central axis of the movable substrate, and compresses fluid by rotation of the rotation shaft, and the rotation A bushing having an insertion hole into which the shaft is inserted, a shaft support member provided with a bearing for a rotating shaft for supporting the rotating shaft in the insertion hole, and an insertion hole into which the eccentric shaft is inserted And the inner circumference of the boss A scroll type compressor having a scroll bearing fitted on the outer peripheral surface of the bush and having a central axis of the movable side substrate and a central axis of the eccentric shaft different from each other, The balancer includes a balancer that rotates integrally with the rotary shaft and has a main weight portion located on the opposite side of the eccentric shaft across the central axis of the rotary shaft, and the bush is fitted on the inner peripheral surface of the scroll bearing. And a cylindrical portion in which the insertion hole is formed in the axial direction, and a secondary weight portion disposed radially outward from the cylindrical portion, wherein the secondary weight portion is arranged in a radial direction of the cylindrical portion. A thin portion extending from the outer peripheral surface of the cylindrical portion, and a thick portion provided outside the thin portion in the radial direction and having a dimension along the axial direction of the rotating shaft larger than the thin portion. And the rotation axis The gist of the present invention is that the entire thick portion is located on the opposite side of the center of the movable-side substrate with respect to the straight line connecting the center of the eccentric shaft and the center of the rotating shaft when viewed from the line direction. Good.

  According to this, it is possible to balance the weight with the movable scroll by the main weight portion of the balancer integrated with the rotating shaft. Since the balancer is separated from the bush, the balancer does not swing at the same time as the bush, and the vibration of the rotating shaft accompanying the swing of the balancer can be suppressed. The center of the movable side substrate and the center of gravity of the movable scroll are substantially the same, and if the entire thick portion is in the region opposite to the center, the center of gravity of the bush is also in that region. For this reason, the moment about the eccentric shaft generated by the centrifugal force acting on the movable scroll with the rotation of the rotating shaft and the moment about the eccentric shaft generated by the centrifugal force acting on the subweight portion with the rotation of the rotating shaft are: Each is in the opposite direction. Therefore, the moment around the eccentric shaft can be canceled and the load applied to the rotary shaft bearing that supports the rotary shaft can be reduced. As a result, the rotary shaft bearing can be downsized.

  In the scroll compressor, the thick portion is disposed so that at least a part thereof faces the outer peripheral surface of the boss portion in the radial direction of the cylindrical portion, and the thin portion is in the axial direction of the rotating shaft May be disposed between the scroll bearing and the rotary shaft.

  According to this, in the bush, the thick portion of the sub weight portion is disposed outside the outer peripheral surface of the boss portion, and the dimension of the thin portion is adjusted to be disposed between the scroll bearing and the rotating shaft. Yes. Therefore, in a bush with a separate balancer, it is possible to reduce the load applied to the rotary shaft bearing while enabling the swing, but without increasing the size, resulting in an increase in the size of the scroll compressor. Absent.

  In the scroll compressor, a back pressure chamber into which a fluid for pressing the movable scroll against the fixed scroll is introduced is formed between the movable side substrate and the shaft support member. The main weight part and the sub-weight part may be arranged in the main body.

  According to this, the main weight part and the sub weight part are arrange | positioned in the back pressure chamber which is the existing structure of a scroll compressor. Therefore, it is not necessary to provide a separate space for accommodating the main weight portion and the sub weight portion, and the scroll compressor is not increased in size because the space for accommodating the main weight portion and the sub weight portion is provided.

  In the scroll compressor, the movable scroll may include a rotation prevention mechanism, and at least a part of the thick portion may be disposed inside the rotation prevention mechanism in the radial direction of the rotation shaft.

  According to this, in the bush, the thick portion of the sub-weight portion is arranged on the inner side of the rotation prevention mechanism, so that the scroll compressor is not enlarged.

  ADVANTAGE OF THE INVENTION According to this invention, while being able to suppress the vibration of the rotating shaft accompanying the swing of a balancer, the load added to the bearing for rotating shafts can be reduced.

1 is a cross-sectional plan view illustrating a scroll compressor according to a first embodiment. The disassembled perspective view which shows a rotating shaft, a balancer, and a bush. FIG. 3 is a cross-sectional view taken along line 3-3 of FIG. Sectional drawing which shows the rotating shaft, balancer, and bush of 2nd Embodiment. The cross-sectional view which shows another example of a scroll compressor.

(First embodiment)
Hereinafter, a first embodiment in which a scroll compressor is embodied will be described with reference to FIGS.

  As shown in FIG. 1, the scroll compressor 10 includes a housing 11 in which a suction port 11a for sucking fluid and a discharge port 11b for discharging fluid are formed. The housing 11 has a substantially cylindrical shape as a whole. The housing 11 includes a bottomed cylindrical motor housing 12 and a compressor housing 13. The motor housing 12 and the compressor housing 13 are assembled in a state where the open ends are abutted with each other. The suction port 11a is provided at a position on the side wall 12a of the motor housing 12, more specifically, on the bottom 12b side of the motor housing 12 in the side wall 12a. The discharge port 11 b is provided in the bottom portion 13 a of the compressor housing 13.

  The scroll compressor 10 includes a rotating shaft 14, a compression unit 15 that compresses the suction fluid sucked from the suction port 11a and discharges the fluid from the discharge port 11b, and an electric motor 16 that drives the compression unit 15. . The rotating shaft 14, the compression unit 15, and the electric motor 16 are accommodated in the housing 11. The electric motor 16 is disposed on the suction port 11 a side in the housing 11, and the compression portion 15 is disposed on the discharge port 11 b side in the housing 11.

  The rotating shaft 14 is accommodated in the housing 11 in a rotatable state. Specifically, a cylindrical shaft support member 21 that supports the rotary shaft 14 is provided in the housing 11. The shaft support member 21 is fixed to the housing 11 at a position between the compression unit 15 and the electric motor 16, for example. A motor housing chamber S is defined in the housing 11 by the shaft support member 21.

  The shaft support member 21 is formed with an insertion hole 23 through which the rotary shaft 14 can be inserted and provided with a first bearing 22 as a rotary shaft bearing. Further, the shaft support member 21 and the bottom portion 12b of the motor housing 12 are opposed to each other, and a cylindrical bearing tube portion 24 projects from the bottom portion 12b. A second bearing 25 is provided inside the bearing tube portion 24. The rotating shaft 14 is supported in a rotatable state by the first bearing 22 and the second bearing 25.

  The compression unit 15 includes a fixed scroll 31 fixed to the housing 11 and a movable scroll 32 that can revolve with respect to the fixed scroll 31 and compresses fluid. The fixed scroll 31 has a disk-shaped fixed side substrate 31a provided on the same axis as the rotary shaft 14, and a fixed side spiral wall 31b rising from the fixed side substrate 31a. Similarly, the movable scroll 32 includes a movable substrate 32a that is disk-shaped and faces the fixed substrate 31a, and a movable spiral wall 32b that stands from the movable substrate 32a toward the fixed substrate 31a. . The movable scroll 32 includes a boss portion 32c that rises in a cylindrical shape from the movable side substrate 32a toward the shaft support member 21. The boss portion 32 c enters the insertion hole 23 of the shaft support member 21. A scroll bearing 17 is provided inside the boss portion 32c. The boss 32c is formed around the central axis N of the movable substrate 32a, and the boss 32c and the movable substrate 32a share the central axis N.

  The fixed scroll 31 and the movable scroll 32 mesh with each other. Specifically, the fixed-side spiral wall 31b and the movable-side spiral wall 32b mesh with each other, and the distal end surface of the fixed-side spiral wall 31b is in contact with the movable-side substrate 32a and the distal end surface of the movable-side spiral wall 32b. Is in contact with the stationary substrate 31a. The fixed scroll 31 and the movable scroll 32 define a compression chamber 33 that compresses fluid.

  The shaft support member 21 is formed with a suction passage 34 for sucking suction fluid into the compression chamber 33. Further, the end surface of the shaft support member 21 is closed by the movable side substrate 32a with the boss portion 32c entering the inner space, and the back pressure chamber 26 is partitioned in the closed space. A high-pressure control gas is introduced into the back pressure chamber 26, and the movable scroll 32 is pressed against the fixed scroll 31 along the direction in which the central axis L of the rotating shaft 14 extends by the control gas. In the following description, the direction in which the central axis L of the rotating shaft 14 extends is referred to as the axial direction.

  The movable scroll 32 is configured to revolve with the rotation of the rotary shaft 14. A part of the rotating shaft 14 protrudes toward the compression portion 15 in the insertion hole 23 of the shaft support member 21. An eccentric shaft 35 is provided at a position that is eccentric with respect to the central axis L of the rotating shaft 14 in the tip of the rotating shaft 14 on the compression unit 15 side. The central axis M of the eccentric shaft 35 is displaced in the radial direction from the central axis L of the rotating shaft 14 and is different from the central axis N of the movable side substrate 32a. A movable scroll 32 is rotatably supported on the eccentric shaft 35 via a bush 36 and a scroll bearing 17.

  The scroll compressor 10 includes a rotation prevention mechanism 28 that allows the revolving motion of the movable scroll 32 and restricts the rotation of the movable scroll 32 when a compression force is applied. A plurality of rotation prevention mechanisms 28 are provided. When the rotating shaft 14 rotates in a predetermined positive direction (clockwise), a revolving motion is performed in which the movable scroll 32 turns in the positive direction. The movable scroll 32 revolves clockwise around the central axis L of the rotary shaft 14. Thereby, since the volume of the compression chamber 33 decreases, the suction fluid sucked into the compression chamber 33 through the suction passage 34 is compressed. The compressed fluid is discharged from the discharge port 30a provided in the fixed side substrate 31a, and then discharged from the discharge port 11b. The fixed side substrate 31a is provided with a discharge valve 30b that covers the discharge port 30a. The fluid compressed in the compression chamber 33 is discharged from the discharge port 30a by pushing away the discharge valve 30b while applying a compressive force to the movable scroll 32.

  The electric motor 16 revolves the movable scroll 32 by rotating the rotating shaft 14. The electric motor 16 includes a rotor 51 that rotates integrally with the rotary shaft 14 and a stator 52 that surrounds the rotor 51. The rotor 51 is connected to the rotating shaft 14. The rotor 51 is provided with a permanent magnet (not shown). The stator 52 is fixed to the inner peripheral surface of the housing 11 (specifically, the motor housing 12). The stator 52 includes a stator core 53 that faces the cylindrical rotor 51 in the radial direction, and a coil 54 wound around the stator core 53. The coil 54 has coil ends 54 a that protrude from both end faces of the stator core 53 along the axial direction of the rotating shaft 14.

  The scroll compressor 10 includes an inverter 55 as a drive circuit that drives the electric motor 16. The inverter 55 is accommodated in a cylindrical cover member 56 attached to the housing 11, specifically, the bottom 12 b of the motor housing 12. The inverter 55 and the coil 54 are electrically connected.

Next, a mechanism for balancing the weight of the revolving motion of the movable scroll 32 will be described.
The eccentric shaft 35 is fitted into a fitting insertion hole 36 a formed in the bush 36. The bush 36 includes a cylindrical portion 37 in which a fitting insertion hole 36 a is formed penetrating in the axial direction, and a subweight portion 43 disposed radially outward from the cylindrical portion 37, and the subweight portion 43 is an outer periphery of the cylindrical portion 37. A thin portion 39 extending from the surface and a thick portion 38 having a thickness along the axial direction of the rotating shaft 14 greater than the thin portion 39 are provided.

  The inner circumferential surface of the cylindrical portion 37 is fitted into the outer circumferential surface of the eccentric shaft 35, and the outer circumferential surface of the cylindrical portion 37 is fitted to the inner circumferential surface of the scroll bearing 17. The bush 36 is rotatably supported by the scroll bearing 17. The center (center axis) of the cylindrical portion 37 coincides with the center of the movable side substrate 32 a when the movable side substrate 32 a is viewed in the axial direction of the rotary shaft 14, and the movable scroll 32 is connected to the rotary shaft 14. Matches the center of gravity when viewed in the axial direction. For this reason, the central axis of the cylindrical portion 37 is referred to as “central axis N”. The center of the cylindrical portion 37 is located on the central axis N when viewed from the axial direction of the rotary shaft 14.

  As shown in FIG. 3, since the eccentric shaft 35 is inserted into the fitting insertion hole 36 a of the bush 36, the central axis of the fitting insertion hole 36 a coincides with the central axis M of the eccentric shaft 35. Therefore, the center axis of the insertion hole 36a is referred to as “center axis M”. The center of the insertion hole 36 a is located on the central axis M when viewed from the axial direction of the rotating shaft 14. The center axis M of the insertion hole 36 a is located outward in the radial direction from the center axis N of the cylindrical portion 37. Specifically, the center axis M of the insertion hole 36a is closer to the subweight portion 43 than the center axis N of the cylindrical portion 37, and is further away from the balancer 40 described later than the center axis N along the radial direction. It is in. When a load is applied to the bush 36 by the revolving motion of the movable scroll 32, the eccentric shaft 35 is located ahead of the central axis N of the cylindrical portion 37, and the eccentric shaft 35 acts to pull the bush 36. .

  The center axis N of the cylindrical portion 37, that is, the center of the cylindrical portion 37 is radially offset with respect to the center axis M of the fitting insertion hole 36 a and the eccentric shaft 35, that is, the center of the fitting insertion hole 36 a and the eccentric shaft 35. In position. When viewed from the axial direction of the rotary shaft 14, the center of the insertion hole 36 a and the eccentric shaft 35 (center axis M) is the center of the rotary shaft 14 (center axis L) and the center of the cylindrical portion 37 (center axis N). Is located closer to the subweight portion 43 than the straight line T.

  As shown in FIG. 1 or FIG. 2, the thin portion 39 of the auxiliary weight portion 43 extends along the radial direction from the portion of the outer peripheral surface of the cylindrical portion 37 that protrudes toward the rotary shaft 14 rather than the scroll bearing 17. It protrudes. The thin portion 39 has a thin plate shape and is disposed closer to the rotating shaft 14 than the scroll bearing 17 in the axial direction of the rotating shaft 14. The thin portion 39 is disposed in a state where the thickness direction extends in the axial direction of the rotating shaft 14, and is disposed between the scroll bearing 17 and the rotating shaft 14.

  The tip of the thin portion 39 in the protruding direction from the cylindrical portion 37 is at a position beyond the outer peripheral surface of the outer ring of the scroll bearing 17 toward the inner peripheral surface of the shaft support member 21. A thick portion 38 is provided at the tip of the thin portion 39. The thick portion 38 is disposed in the back pressure chamber 26 radially outside the outer peripheral surface of the boss portion 32 c, and is disposed between the outer peripheral surface of the boss portion 32 c and the inner peripheral surface of the shaft support member 21. For this reason, the thick portion 38 is disposed so that a part thereof faces the outer peripheral surface of the boss portion 32 c in the radial direction of the cylindrical portion 37. Further, a part of the thick portion 38 is disposed inside the rotation prevention mechanism 28 in the radial direction of the rotating shaft 14.

  The dimension of the thick part 38 along the axial direction of the rotating shaft 14 is larger than the dimension of the thin part 39 along the axial direction of the rotating shaft 14. In other words, the dimension of the thin portion 39 along the axial direction of the rotary shaft 14 is smaller than the dimension of the thick portion 38 along the axial direction of the rotary shaft 14. That is, the thin portion 39 is disposed between the scroll bearing 17 and the rotary shaft 14 in the axial direction of the rotary shaft 14 and is thinner in the axial direction of the rotary shaft 14 than the thick portion 38.

  The block-shaped thick portion 38 includes a first portion 38 a that protrudes toward the movable scroll 32 from the thin portion 39 and a second portion 38 b that protrudes toward the rotating shaft 14 from the thin portion 39. The dimension of the first portion 38 a along the radial direction of the rotating shaft 14 is smaller than the dimension of the second portion 38 b along the radial direction of the rotating shaft 14. The dimension of the second portion 38 b along the radial direction of the rotation shaft 14 is constant in the axial direction of the rotation shaft 14. The second portion 38b is located closer to the electric motor 16 than the end surface of the rotating shaft 14 on the compression portion 15 side, and overlaps with a part of the rotating shaft 14 in the radial direction.

  As shown in FIG. 3, when the bush 36 is viewed in the axial direction of the rotary shaft 14, the center of gravity Z of the bush 36 exists on the thin portion 39 of the subweight portion 43 and is thicker than the central axis N of the cylindrical portion 37. It exists near the thick portion 38. Here, a plane in which the center of gravity Z of the bush 36 and the center of gravity X of the subweight portion 43 exist is assumed as a virtual plane passing through the cross section along the radial direction of the rotating shaft 14. When the bush 36 is viewed in the axial direction of the rotary shaft 14, the center of gravity Z of the bush 36 and the center of gravity X of the subweight portion 43 are eccentric with respect to the straight line T when the virtual plane is separated from the straight line T. It is located on the same side as the center of 35 (center axis M). Further, as viewed from the axial direction of the rotary shaft 14, the entire thick portion 38 is located on the same side as the center (center axis M) of the eccentric shaft 35 with respect to the straight line T.

  A straight line Lb connecting the center of the eccentric shaft 35 (center axis M) and the center of the rotation shaft 14 (center axis L) is assumed. When viewed from the axial direction of the rotary shaft 14, the entire thick portion 38 is located on the opposite side of the center of the movable side substrate 32 a, that is, the center of the cylindrical portion 37 (center axis N) with respect to the straight line Lb. The center of the movable substrate 32 a coincides with the center of gravity of the movable scroll 32. For this reason, the entire thick portion 38 is located in the center of the movable side substrate 32a (the center of the cylindrical portion 37) with respect to the straight line Lb, and thus in a region opposite to the center of gravity of the movable side substrate 32a. The center of gravity Z is also located.

  The bush 36 configured as described above swings when the scroll compressor 10 is started or when a change in conditions such as a change in the speed of the movable scroll 32 occurs. By the swing of the bush 36, the revolution radius of the movable scroll 32 is variable, and the contact pressure between the fixed spiral wall 31b and the movable spiral wall 32b is appropriately maintained. Note that the swing range of the bush 36 is restricted by contact between a concave portion 41a and a second portion 38b, which will be described later.

  A balancer 40 is integrally fixed to the rotating shaft 14. The balancer 40 includes a balancer main body 41 as a main weight portion having a semicircular shape when viewed in the axial direction of the rotary shaft 14, and a holding portion having a semicircular shape for fixing the balancer 40 to the rotary shaft 14 together with the balancer main body 41. 42. The balancer body 41 is formed with a recess 41a in which a part of the end surface on the movable scroll 32 side is recessed. Of the thick part 38 of the bush 36, the second part 38 b enters the recess 41 a of the balancer body 41. The thick portion 38 included in the bush 36 has a smaller volume and a smaller weight than the balancer 40. The recess 41a allows the thick portion 38 to swing.

  When the balancer 40 is viewed in the axial direction of the rotary shaft 14, the center of gravity V of the balancer 40 exists on the opposite side of the center of the cylindrical portion 37 (center axis N) across the center of the rotary shaft 14 (center axis L). is doing. Since the center axis N of the cylindrical portion 37 coincides with the center of gravity of the movable scroll 32, the center of gravity V of the balancer 40 exists on the opposite side of the center of gravity of the movable scroll 32 across the center axis L of the rotary shaft 14. The balancer body 41 is located on the opposite side of the eccentric shaft 35 with the central axis L of the rotating shaft 14 in between.

  During the revolving motion of the movable scroll 32, the movable scroll 32 receives a centrifugal force Fa on the side opposite to the balancer body 41. At the same time, the balancer body 41 receives a centrifugal force Fc on the side opposite to the movable scroll 32. Therefore, during the revolving motion of the movable scroll 32, the centrifugal force Fa acting on the movable scroll 32 is canceled out by the centrifugal force Fc acting on the balancer body 41, and the weight balance with the movable scroll 32 is achieved. .

  In FIG. 3, the rotating shaft 14 rotates clockwise, and accordingly, the balancer body 41 also rotates clockwise. Due to the contact between the concave portion 41a and the second portion 38b, the auxiliary weight portion 43 rotates integrally with the balancer body 41 in the clockwise direction. On the other hand, when the movable scroll 32 revolves clockwise, a moment Ma due to the centrifugal force Fa acting on the movable scroll 32 is generated around the eccentric shaft 35. The direction of the moment Ma is the same as the direction of revolution of the movable scroll 32 and the direction of rotation of the rotary shaft 14. Therefore, a clockwise moment Ma acts on the cylindrical portion 37 around the eccentric shaft 35.

  On the other hand, due to the rotation of the rotating shaft 14, the subweight portion 43 receives the centrifugal force Fb around the eccentric shaft 35 and a moment Mb is generated. The direction of the moment Mb is opposite to the rotation direction of the rotary shaft 14 and is counterclockwise. Here, as viewed from the axial direction of the rotary shaft 14, the entire subweight portion 43 including the center of gravity Z of the subweight portion 43 is located on the same side as the center of the eccentric shaft 35 with respect to the straight line T. For this reason, the moment Mb around the eccentric shaft 35 generated by the centrifugal force Fb acting on the subweight portion 43 can be further increased. Therefore, the clockwise moment Ma generated around the eccentric shaft 35 by the revolving motion of the movable scroll 32, that is, the moment Ma due to the centrifugal force Fa acting on the movable scroll 32 is eccentric by the centrifugal force Fb acting on the subweight portion 43. The counterclockwise moment Mb generated around the shaft 35 is offset, and as a result, the vibration of the rotating shaft 14 is reduced. The fitting insertion hole 36 a of the bush 36 is formed at a position where the moment Ma caused by the centrifugal force Fa acting on the movable scroll 32 and the moment Mb caused by the centrifugal force Fb acting on the subweight portion 43 are in opposite directions. .

  Note that the entire thick portion 38 of the bush 36 is located on the opposite side of the center (central axis N) of the movable substrate 32a with respect to the straight line Lb when viewed from the axial direction of the rotary shaft 14. As a result, the center of gravity Z of the bush 36 is also located on the opposite side of the center of the movable side substrate 32a, and hence the center of gravity of the movable scroll 32, with respect to the straight line Lb. That is, the center of gravity of the movable scroll 32 and the center of gravity Z of the bush 36 are located on the opposite sides of the straight line Lb when viewed from the axial direction of the rotary shaft 14.

  The vector of the centrifugal force Fa acting on the movable scroll 32 is substantially located on a straight line connecting the center (center axis L) of the rotating shaft 14 and the center (center axis N) substantially equal to the center of gravity of the movable substrate 32a. The vector of the centrifugal force Fb acting on the subweight portion 43 is along a straight line connecting the center of the rotating shaft 14 (center axis N) and the center of gravity Z of the bush 36. The center of gravity (center axis N) of the movable substrate 32a and the center of gravity Z of the bush 36 are located on the opposite sides of the straight line Lb, respectively, and the center (center axis) of the eccentric shaft 35 that generates centrifugal force acting on them. M) The moment Ma and the moment Mb are in opposite directions.

  In order to avoid interference between the thick portion 38 of the auxiliary weight portion 43 and the scroll bearing 17, it is necessary to extend the tip of the thin portion 39 to a position beyond the outer peripheral surface of the boss portion 32 c. The length of the thin portion 39 along the radial direction is determined. The weight of the sub-weight portion 43 is set so that the moment determined by the length of the thin portion 39 and the weight of the thick portion 38 is such that the moment due to the revolving motion of the movable scroll 32 can be offset. And the adjustment of the weight of the subweight part 43 is performed by adjusting the dimension of the thick part 38 along the axial direction of the rotating shaft 14.

Next, the operation of the scroll compressor 10 will be described.
When the rotating shaft 14 is rotated by supplying electric power to the electric motor 16, the bush 36 revolves around the rotating shaft 14 and the movable scroll 32 revolves. Further, the balancer 40 rotates integrally with the rotating shaft 14. Then, the centrifugal force Fa acting on the movable scroll 32 is offset by the centrifugal force Fc acting on the balancer body 41.

In addition, when the movable scroll 32 revolves or when conditions such as a speed change change, the bush 36 swings to adjust the revolving radius of the movable scroll 32.
According to the first embodiment, the following effects can be obtained.

  (1-1) The balancer 40 is provided integrally with the rotary shaft 14, and the balance with the movable scroll 32 is balanced by the balancer body 41 of the balancer 40. Since the balancer 40 is separated from the bush 36, the balancer 40 is prevented from swinging simultaneously with the bush 36, and the vibration of the rotating shaft 14 accompanying the swing of the balancer 40 can be suppressed.

  Then, the center of gravity Z of the bush 36 is positioned on the same side as the center (center axis M) of the eccentric shaft 35 with respect to the straight line T, and centrifugal force Fb acts on the bush 36 on the subweight portion 43 side with respect to the straight line T. I tried to do it. Further, the auxiliary weight portion 43 is provided in the bush 36, and the position of the fitting insertion hole 36a of the bush 36 is set to the moment Ma due to the centrifugal force Fa acting on the movable scroll 32 and the moment due to the centrifugal force Fb acting on the auxiliary weight portion 43. It was provided at a position where Mb was in the opposite direction. Thereby, even if a moment arises around the eccentric shaft 35, it can cancel, the load added to the 1st bearing 22 which supports the rotating shaft 14 can be reduced, and the 1st bearing 22 can be reduced in size. Further, by positioning the center of gravity Z of the bush 36 on the same side as the center (center axis M) of the eccentric shaft 35 with respect to the straight line T, the center of gravity Z of the bush 36 around the eccentric shaft 35 generated by the centrifugal force Fb acting on the subweight portion 43 is obtained. The moment Mb can be increased. As a result, the sub weight portion 43 can be reduced in size.

  (1-2) The balancer 40 is rotated integrally with the rotary shaft 14. Since the swing of the balancer 40 can be eliminated, it is not necessary to reduce the weight in consideration of the swing of the balancer 40 and the weight balance with the movable scroll 32 can be easily achieved.

  (1-3) A balancer body 41 for balancing the weight with the movable scroll 32 is disposed in the back pressure chamber 26. Since the back pressure chamber 26 is an existing space provided in the scroll compressor 10, it does not increase the size of the shaft support member 21 and consequently does not increase the size of the scroll compressor 10.

  (1-4) The subweight portion 43 of the bush 36 is disposed in the back pressure chamber 26, and the balancer 40 and the subweight portion 43 are disposed in the back pressure chamber 26. Since the back pressure chamber 26 is an existing space provided in the scroll compressor 10, there is no need to newly provide a space for accommodating the balancer 40 and the auxiliary weight portion 43, and the balancer 40 and the auxiliary weight portion 43 are accommodated. There is no increase in the size of the scroll compressor 10 due to the space.

  (1-5) In the bush 36, the thin portion 39 is thinner than the thick portion 38, and the thick portion 38 has a block shape. The thin portion 39 and the thick portion 38 have a smaller volume and a smaller weight than the balancer 40. Therefore, compared with the case where the balancer 40 is provided integrally with the cylindrical portion 37 of the bush 36, the fluctuation of the weight balance due to the swing of the sub weight portion 43 can be reduced, and the vibration of the rotating shaft 14 can be suppressed.

(1-6) Since the concave portion 41a is provided in the balancer 40, the auxiliary weight portion 43 can be extended in the axial direction of the rotating shaft 14, and the weight of the auxiliary weight portion 43 can be easily adjusted.
(1-7) The subweight portion 43 of the bush 36 has a thick portion 38 and a thin portion 39, and the subweight portion 43 is on the same side as the center of the eccentric shaft 35 (center axis M) with respect to the straight line T. Is located. When the bush 36 is assembled to the rotary shaft 14, the center of gravity Z of the bush 36 with respect to the straight line T is adjusted with respect to the eccentric shaft 35 even if the position of the bush 36 slightly varies due to the manufacturing tolerance or assembly tolerance of the bush 36. It can be located on the same side as the center.

  (1-8) When viewed from the axial direction of the rotating shaft 14, the entire subweight portion 43 including the center of gravity X of the subweight portion 43 is located on the same side as the center of the eccentric shaft 35 with respect to the straight line T. . For this reason, the moment Mb around the eccentric shaft 35 generated by the centrifugal force Fb acting on the subweight portion 43 can be further increased, and as a result, the subweight portion 43 can be reduced in size.

  (1-9) The sub-weight part 43 of the bush 36 has a thick part 38 and a thin part 39, and the thick part 38 is disposed inside the rotation prevention mechanism 28 in the radial direction of the rotating shaft 14. Therefore, the scroll compressor 10 is not enlarged.

  (1-10) When viewed from the axial direction of the rotating shaft 14, the entire thick portion 38 of the bush 36 is located on the opposite side to the center (central axis N) of the movable substrate 32 a with respect to the straight line Lb. . As a result, the center of gravity Z of the bush 36 is also located on the opposite side of the center of the movable side substrate 32a, and hence the center of gravity of the movable scroll 32, with respect to the straight line Lb. The vector of the centrifugal force Fa acting on the movable scroll 32 is substantially located on a straight line connecting the center (center axis L) of the rotating shaft 14 and the center (center axis N) substantially equal to the center of gravity of the movable substrate 32a. The vector of the centrifugal force Fb acting on the subweight portion 43 is along a straight line connecting the center of the rotating shaft 14 (center axis N) and the center of gravity Z of the bush 36. The center of gravity (center axis N) of the movable substrate 32a and the center of gravity Z of the bush 36 are located on the opposite sides of the straight line Lb, respectively, and the center (center axis) of the eccentric shaft 35 that generates centrifugal force acting on them. M) The moment Ma and the moment Mb are in opposite directions. As a result, the sub weight portion 43 can be reduced in size.

(Second Embodiment)
Next, a second embodiment in which the scroll compressor is embodied will be described with reference to FIG. In the second embodiment, detailed description of the same or overlapping portions as those in the first embodiment is omitted.

  As shown in FIG. 4, the center (center axis M) of the insertion hole 36 a and the eccentric shaft 35 is positioned more radially outward than the center (center axis N) of the cylindrical portion 37. Specifically, when viewed from the axial direction of the rotating shaft 14, the center of the fitting insertion hole 36 a is closer to the subweight portion 43 than the center of the cylindrical portion 37, and the balancer 40 is more than the central axis N along the radial direction. It is in a position approaching. And the center of the cylindrical part 37 exists in the position offset in the radial direction with respect to the center of the fitting insertion hole 36a. The center of the insertion hole 36 a is located closer to the subweight portion 43 than the straight line T connecting the center of the rotating shaft 14 and the center of the cylindrical portion 37.

  The length of the line segment La connecting the center of the cylindrical portion 37 (center axis N) and the center of the eccentric shaft 35 (center axis M) is the same as the center (center axis N) of the cylindrical portion 37 in the first embodiment. It is longer than the line connecting the center of the shaft 35 (center axis M). For this reason, the fitting insertion hole 36a and the eccentric shaft 35 are located closer to the central axis L on the end surface of the rotary shaft 14 than in the first embodiment. When a load is applied to the bush 36 by the revolving motion of the movable scroll 32, the eccentric shaft 35 acts to push the cylindrical portion 37. Further, when the bush 36 is viewed in the axial direction of the rotary shaft 14, the center of gravity Z of the bush 36 is the center of the eccentric shaft 35 (the center axis M) when the virtual plane is divided with the straight line T as a boundary. ) Is located on the same side.

  In the above configuration, during the revolving motion of the movable scroll 32, the centrifugal force Fa acting on the movable scroll 32 is received as the rotary shaft 14 rotates, and a moment Ma is generated around the eccentric shaft 35. This moment Ma is opposite to the rotation direction of the rotating shaft 14. At the same time, during the revolving motion of the movable scroll 32, the centrifugal force Fb acting on the subweight portion 43 is received as the rotary shaft 14 rotates, and a moment Mb is generated around the eccentric shaft 35. This moment Mb is in the same direction as the rotation direction of the rotary shaft 14. Therefore, the moment Ma caused by the centrifugal force Fa acting on the movable scroll 32 is opposite to the moment Mb caused by the centrifugal force Fb acting on the subweight portion 43. The fitting insertion hole 36 a of the bush 36 is formed at a position where the moment Ma caused by the centrifugal force Fa acting on the movable scroll 32 and the moment Mb caused by the centrifugal force Fb acting on the subweight portion 43 are in opposite directions. . Specifically, when viewed from the axial direction of the rotating shaft 14, the entire thick portion 38 of the bush 36 connects the center of the eccentric shaft 35 (center axis M) and the center of the rotating shaft 14 (center axis L). It is located on the opposite side to the center (central axis N) of the movable substrate 32a with respect to the straight line Lb. That is, the center of gravity of the movable scroll 32 and the center of gravity Z of the bush 36 are located on the opposite sides of the straight line Lb when viewed from the axial direction of the rotary shaft 14. As a result, the two moments Ma and Mb are canceled out.

According to the said 2nd Embodiment, in addition to the effect similar to description to (1-1)-(1-10) of 1st Embodiment, the following effects can be acquired.
(2-1) A line segment La connecting the center of the cylindrical portion 37 (center axis N) and the center of the eccentric shaft 35 (center axis M) is longer than that in the first embodiment. For this reason, even if the angle when the bush 36 swings is small, the turning radius of the movable scroll 32 can be adjusted.

Each embodiment can be implemented with the following modifications. The present embodiment and the following modifications can be implemented in combination with each other within a technically consistent range.
In each embodiment, when the bush 36 is viewed in the axial direction of the rotary shaft 14, if the center of gravity Z of the bush 36 is located on the same side as the center (center axis M) of the eccentric shaft 35 with respect to the straight line T, You may change the dimension of the thin part 39 along the axial direction of the rotating shaft 14, and the dimension of the thin part 39 along the radial direction of the rotating shaft 14. FIG. Moreover, in the subweight part 43, the dimension along the axial direction of the rotating shaft 14 may be made constant, and the subweight part 43 may be configured without the thick part 38 and the thin part 39.

  As shown in FIG. 5, in the second embodiment, the balancer 40 is disposed in a space between the electric motor 16 and the shaft support member 21 along the axial direction of the rotating shaft 14 in the motor storage chamber S. The back pressure chamber 26 may not be present. The balancer 40 is integrated with the rotating shaft 14 by a holding portion 42.

  In the case of such a configuration, the back pressure chamber 26 is reduced along the axial direction of the rotary shaft 14 by the amount that the balancer 40 is eliminated, compared with the case where the balancer 40 is disposed in the back pressure chamber 26, and the first bearing 22. Can be moved closer to the movable scroll 32. As a result, the distance between the first bearing 22 and the second bearing 25 along the axial direction of the rotating shaft 14 can be increased, and the distance between the first bearing 22 and the scroll bearing 17 can be decreased. As a result, the load applied to the first bearing 22 and the second bearing 25 due to the compressive force and centrifugal force acting on the movable scroll 32 can be reduced.

In the first embodiment, the balancer body 41 of the balancer 40 may be disposed outside the back pressure chamber 26, for example, in the motor housing chamber S.
In each embodiment, the balancer 40 and the rotary shaft 14 are separate members, and the balancer 40 is held by the rotary shaft 14 by the holding portion 42 so that the balancer 40 and the rotary shaft 14 are integrated. The main body 41 may be integrally formed as one member.

  In each embodiment, the entire thick portion 38 may be disposed so as to face the outer peripheral surface of the boss portion 32c in the radial direction of the cylindrical portion 37. In other words, the thick portion 38 may include only the first portion 38a.

  In each embodiment, the entire thick portion 38 may be disposed inside the rotation prevention mechanism 28 in the radial direction of the rotating shaft 14. In other words, the thick portion 38 may include only the first portion 38a.

In each embodiment, the thick part 38 is not divided into the first part 38a and the second part 38b, and the dimension along the axial direction of the rotary shaft 14 may be the same in the whole thick part 38. .
In the bush 36 of each embodiment, the fitting insertion hole 36 a may not penetrate the cylindrical portion 37.

In each embodiment, the scroll compressor 10 may be a type that does not include the back pressure chamber 26.
In each embodiment, the center of gravity of the movable scroll 32 and the center of gravity Z of the bush 36 are opposite to the straight line connecting the center of the eccentric shaft 35 and the center of the rotating shaft 14 when viewed from the axial direction of the rotating shaft 14. It may be located on the side.

  L: Center axis of rotating shaft, N: Center axis of movable substrate and cylindrical part (center of gravity of movable scroll), M: Center axis of eccentric shaft, T: Straight line, V: Center of gravity of balancer, X: Subweight Center of gravity, Z ... Center of gravity of bush, 10 ... Scroll compressor, 14 ... Rotating shaft, 17 ... Scroll bearing, 21 ... Shaft support member, 22 ... First bearing as bearing for rotating shaft, 23 ... Insertion hole, 26 ... back pressure chamber, 28 ... anti-rotation mechanism, 31 ... fixed scroll, 31a ... fixed side substrate, 31b ... fixed side spiral wall, 32 ... movable scroll, 32a ... movable side substrate, 32b ... movable side spiral wall, 32c ... boss 35: Eccentric shaft, 36: Bush, 36a ... Insertion hole, 37 ... Cylindrical part, 38 ... Thick part, 39 ... Thin part, 40 ... Balancer, 41 ... Balancer body as main weight part, 43 ... Deputy Weight part.

Claims (8)

A rotation axis;
An eccentric shaft provided at the tip of the rotating shaft;
A fixed scroll having a fixed side substrate, and a fixed side spiral wall standing upright from the fixed side substrate;
From the movable side substrate that is disc-shaped and faces the fixed side substrate, the movable side spiral wall that stands up from the movable side substrate toward the fixed side substrate and meshes with the fixed side spiral wall, and the movable side substrate A movable scroll that rises toward the rotating shaft and has a cylindrical boss formed around a central axis of the movable substrate, and compresses fluid by rotation of the rotating shaft;
A shaft support member having an insertion hole through which the rotation shaft is inserted, and provided with a bearing for a rotation shaft for supporting the rotation shaft in the insertion hole;
A bush having an insertion hole into which the eccentric shaft is inserted;
A scroll bearing externally fitted to the inner peripheral surface of the boss portion and internally fitted to the outer peripheral surface of the bush;
The center axis of the movable substrate and the center axis of the eccentric shaft are different scroll compressors,
A balancer having a main weight portion that rotates integrally with the rotation shaft and is located on the opposite side of the eccentric shaft across the central axis of the rotation shaft;
The bush is externally fitted on the inner peripheral surface of the scroll bearing, and the cylindrical portion in which the insertion hole is formed in the axial direction;
A sub-weight portion disposed radially outward from the cylindrical portion, and
The insertion hole is generated by a moment around the eccentric shaft generated by a centrifugal force acting on the movable scroll with the rotation of the rotating shaft and a centrifugal force acting on the subweight portion with the rotation of the rotating shaft. The moments around the eccentric shaft are respectively provided at positions in opposite directions,
The center of gravity of the bush is located on the same side as the center of the eccentric shaft with respect to a straight line connecting the center of the cylindrical portion and the center of the rotational shaft as viewed from the axial direction of the rotation shaft. Scroll type compressor.   The center of gravity of the sub-weight portion is located on the same side as the center of the eccentric shaft with respect to a straight line connecting the center of the cylindrical portion and the center of the rotation shaft, as viewed from the axial direction of the rotation shaft. The scroll compressor described in 1.   The whole of the sub-weight portion is located on the same side as the center of the eccentric shaft with respect to a straight line connecting the center of the cylindrical portion and the center of the rotation shaft when viewed from the axial direction of the rotation shaft. The scroll compressor described in 1.   The sub-weight portion is provided with a thin portion extending from the outer peripheral surface of the cylindrical portion along the radial direction of the cylindrical portion, a dimension provided on the outer side in the radial direction with respect to the thin portion, and a dimension along the axial direction of the rotating shaft Has a thicker portion larger than the thinned portion, and when viewed from the axial direction of the rotating shaft, the entire thickened portion is in the straight line connecting the center of the cylindrical portion and the center of the rotating shaft. On the other hand, the scroll compressor according to any one of claims 1 to 3, which is located on the same side as the center of the eccentric shaft. A rotation axis;
An eccentric shaft provided at the tip of the rotating shaft;
A fixed scroll having a fixed side substrate, and a fixed side spiral wall standing upright from the fixed side substrate;
From the movable side substrate that is disc-shaped and faces the fixed side substrate, the movable side spiral wall that stands up from the movable side substrate toward the fixed side substrate and meshes with the fixed side spiral wall, and the movable side substrate A movable scroll that rises toward the rotating shaft and has a cylindrical boss formed around a central axis of the movable substrate, and compresses fluid by rotation of the rotating shaft;
A shaft support member having an insertion hole through which the rotation shaft is inserted, and provided with a bearing for a rotation shaft for supporting the rotation shaft in the insertion hole;
A bush having an insertion hole into which the eccentric shaft is inserted;
A scroll bearing externally fitted to the inner peripheral surface of the boss portion and internally fitted to the outer peripheral surface of the bush;
The center axis of the movable substrate and the center axis of the eccentric shaft are different scroll compressors,
A balancer having a main weight portion that rotates integrally with the rotation shaft and is located on the opposite side of the eccentric shaft across the central axis of the rotation shaft;
The bush is externally fitted on the inner peripheral surface of the scroll bearing, and the cylindrical portion in which the insertion hole is formed in the axial direction;
A sub-weight portion disposed radially outward from the cylindrical portion, and
The sub-weight portion is provided with a thin portion extending from the outer peripheral surface of the cylindrical portion along the radial direction of the cylindrical portion, a dimension provided on the outer side in the radial direction than the thin portion, and a dimension along the axial direction of the rotating shaft Has a thicker portion larger than the thinned portion, and when viewed from the axial direction of the rotating shaft, the entire thickened portion is relative to a straight line connecting the center of the eccentric shaft and the center of the rotating shaft. A scroll compressor located on the opposite side of the center of the movable substrate.   The thick portion is disposed so that at least a part thereof faces the outer peripheral surface of the boss portion in the radial direction of the cylindrical portion, and the thin portion is configured to rotate with the scroll bearing in the axial direction of the rotating shaft. The scroll compressor according to claim 4 or 5, which is arranged between the shaft.   A back pressure chamber into which a fluid for pressing the movable scroll toward the fixed scroll is introduced is formed between the movable side substrate and the shaft support member, and the main weight portion and the sub weight chamber are formed in the back pressure chamber. The scroll compressor according to claim 6, wherein a weight portion is disposed.   The scroll type according to claim 6 or 7, wherein the movable scroll includes a rotation prevention mechanism, and the thick portion is disposed at least partially inside the rotation prevention mechanism in a radial direction of the rotation shaft. Compressor.