JP2017145806A - Scroll compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To increase the shape dimension of a balance weight without causing area reduction of a thrust bearing surface and strength reduction of a bearing member.SOLUTION: A scroll compressor comprises an annular thrust plate 32 which is installed inside a housing and has a thrust bearing surfaces 32S contacting with the back surface of the end plate 21A of an orbital scroll 21, and a main balance weight 41 which is provided on a drive shaft 9 to be axially adjacent to the thrust plate 32 and cancels centrifugal force associated with eccentric orbiting motion of the orbital scroll 21. The balance weight 41 has, at its end on the thrust plate 32 side, an outer diameter reduction portion 41a which is gradually reduced in the outer diameter toward the thrust plate 32 side. The thrust plate 32 has, on its inner diameter portion on the main balance weight 41 side, an inner diameter increase portion 32a which is gradually increased in the inner diameter toward the main balance weight 41 side. The outer diameter reduction portion 41a and the inner diameter increase portion 32a overlap in the radial direction and in the axial direction.SELECTED DRAWING: Figure 2

Description

  The present invention relates to a scroll compressor that compresses a refrigerant.

  As shown in FIG. 1 of Patent Document 1, a scroll compressor that compresses a refrigerant includes a compression mechanism including a fixed scroll fixed inside a housing and a turning scroll that meshes with the fixed scroll. . A cylindrical boss is formed at the center of the rear surface of the end plate of the orbiting scroll, and a drive bush is rotatably fitted to the boss through a bearing. Further, an eccentric pin (crank pin) of the drive shaft is fitted to the drive bush. ) Is fitted. Further, the rotation of the orbiting scroll is regulated by an Oldham ring (a rotation prevention mechanism).

  When the drive shaft is rotationally driven by a drive source such as an engine or a motor, the orbiting scroll makes an eccentric orbiting motion with respect to the fixed scroll while its rotation is restricted. As a result, the volume of the compression space formed between the two scrolls changes continuously, the refrigerant is sucked from the suction port when the volume is expanded, the refrigerant is compressed when the volume is reduced, and is compressed at the timing after the maximum compression. The refrigerant is discharged from the discharge port.

  As described above, the orbiting scroll makes an eccentric orbiting motion with respect to the fixed scroll, so that if it remains as it is, rotational vibration is generated on the drive shaft due to the weight imbalance. In order to eliminate this weight imbalance, the drive bush or the drive shaft itself is provided with a balance weight in which a weight is arranged in a direction opposite to the eccentric direction of the orbiting scroll, and the centrifugal force accompanying the eccentric orbiting motion of the orbiting scroll is provided. It cancels out to suppress rotational vibration.

  During operation of the scroll compressor, the orbiting scroll is pressed in the direction away from the fixed scroll (thrust direction) by the reaction force of the compressed refrigerant. To receive the thrust force, an annular thrust plate (thrust bearing) is installed inside the housing. The rear surface of the end plate of the orbiting scroll slides relative to the thrust bearing surface of the thrust plate, and by increasing the area of this thrust bearing surface, the thrust load per unit area is reduced and the oil film between both members is formed. Thus, the turning scroll can be smoothly eccentrically swung, and the end plates of the turning scroll and the thrust plate can be prevented from being worn.

JP 2011-214474 A

  In such a scroll compressor, in order to increase the capacity of the compression mechanism, it is necessary to increase the diameters of the fixed scroll and the orbiting scroll, or to increase the eccentric amount of the orbiting scroll with respect to the fixed scroll. Thereby, the centrifugal force accompanying the eccentric turning motion of the turning scroll increases. Accordingly, it is necessary to increase the size and shape of the balance weight provided in the drive bush and increase the weight weight to counter the centrifugal force of the orbiting scroll.

  In order to increase the size and shape of the balance weight, it is necessary to expand the space around the drive bush where the balance weight is installed in the axial direction and the radial direction. However, in this case, the inner diameter of the annularly formed thrust plate has to be increased, and as a result, the area of the thrust bearing surface where the orbiting scroll and the thrust plate come into contact is reduced, and the thrust load per unit area is reduced. Increased sliding heat generation.

  In addition, due to the increase in the size and shape of the balance weight, the thickness of the bearing member that pivotally supports the intermediate portion of the drive shaft must be made relatively thin, and securing the strength of the main bearing and reducing the amount of deflection are issues. It becomes.

  The present invention has been made in view of such circumstances, and with a simple configuration, the size and shape of the balance weight is increased without reducing the area of the thrust bearing surface and reducing the strength of the bearing member. An object of the present invention is to provide a scroll compressor that can cope with an increase in capacity of a compression mechanism.

In order to solve the above problems, the present invention employs the following means.
That is, the scroll compressor according to the present invention is provided with a fixed scroll fixed inside the housing, a turning scroll meshing with the fixed scroll, a drive shaft for moving the turning scroll eccentrically, and an inside of the housing. A bearing member that supports the drive shaft, an annular thrust plate that is installed inside the housing and whose thrust surface is in contact with the rear surface of the end plate of the orbiting scroll and receives a thrust force acting on the orbiting scroll, and A main balance weight that is provided on the drive shaft and is adjacent to the thrust plate in the axial direction, and cancels centrifugal force associated with the eccentric orbiting motion of the orbiting scroll, and the main balance weight is provided on the thrust plate side. At the end, the outer diameter decreases toward the thrust plate. The thrust plate has an inner diameter enlarged portion whose inner diameter increases toward the main balance weight side on the main balance weight side of the inner diameter portion, and the outer diameter reduced portion and the thrust plate The inner diameter enlarged portion overlaps the radial direction and the axial direction.

  According to the above configuration, the inner diameter of the thrust plate is increased from the thrust bearing surface side toward the main balance weight side by the inner diameter enlarged portion. For this reason, the volume of the accommodation chamber of the main balance weight adjacent to the thrust plate can be expanded in both the radial direction and the axial direction while maintaining the area of the thrust bearing surface at a predetermined size.

  On the other hand, the outer diameter reduced portion of the main balance weight overlaps the radially inner portion of the thrust plate in the radial direction and the axial direction. For this reason, the radial dimension can be increased while extending the axial dimension of the main balance weight toward the thrust plate.

  Therefore, without reducing the area of the thrust bearing surface in the thrust plate, the size and shape of the main balance weight can be increased to cope with the increase in the capacity of the compression mechanism.

  In the scroll compressor having the above-described configuration, the outer diameter reduction portion may have an outer conical surface shape, and the inner diameter enlargement portion may have an inner conical surface shape that faces the outer diameter reduction portion in parallel with an interval.

  Alternatively, the outer diameter reduced portion may be an outer stepped cylindrical surface shape having at least one step portion, and the inner diameter enlarged portion may be an inner stepped cylindrical surface shape that meshes with the outer diameter reduced portion at an interval. Good.

  By doing so, the outer diameter reduced portion of the main balance weight can be easily brought closer to the inner diameter enlarged portion of the thrust plate to increase the size and shape of the main balance weight, which can cope with the increase in the capacity of the compression mechanism.

  In the scroll compressor having the above configuration, the main balance weight is provided so as to be adjacent to the bearing member in the axial direction, and has an inner peripheral overlap portion that overlaps the radially inner peripheral side of the bearing member, The inner circumferential overlap portion has an outer diameter reduction portion whose outer diameter gradually decreases in the axial direction toward the radial bearing portion of the bearing member, and the bearing member is directed toward the inner circumferential overlap portion. It is good also as a structure which has an internal diameter expansion part which an internal diameter increases gradually, and the said outer diameter reduction part and the said internal diameter expansion part overlap in an axial direction and radial direction.

  According to the above configuration, the outer diameter of the bearing member changes in a conical cylinder shape toward the inner peripheral overlap portion of the balance weight at the inner diameter enlarged portion. For this reason, compared with the case where the part of an internal diameter expansion part is comprised with the plane orthogonal to an axial direction and the cylindrical surface parallel to an axial direction, a thin part does not generate | occur | produce in a bearing member. Therefore, with a simple configuration, it is possible to increase the size and shape of the balance weight (inner peripheral overlap portion) without reducing the strength of the bearing member, and to cope with an increase in the capacity of the compression mechanism.

  The scroll compressor having the above-described configuration further includes a sub-balance weight separate from the main balance weight, and the sub-balance weight is positioned on the opposite side of the main balance weight with respect to the bearing member in the axial direction. It is provided so that it may adjoin and it has an outer peripheral overlap part which overlaps with the diameter direction outer peripheral side of this bearing member, and this inner peripheral overlap part gradually increases an inner diameter toward the fixed part side of this bearing member in the axial direction The bearing member has an outer diameter reducing portion in which an outer diameter gradually decreases toward the outer peripheral overlap portion, and the inner diameter expanding portion and the outer diameter reducing portion are arranged in an axial direction and a diameter. It is good also as a structure which overlaps with a direction.

  According to the above configuration, the outer diameter of the bearing member changes in a conical cylinder shape toward the outer peripheral overlap portion of the balance weight at the outer diameter reducing portion. For this reason, compared with the case where the part of an outer diameter reduction part is comprised with the plane orthogonal to an axial direction and the cylindrical surface parallel to an axial direction, a thin part does not generate | occur | produce in a bearing member. Therefore, with a simple configuration, it is possible to increase the size and shape of the balance weight (peripheral overlap portion) without reducing the strength of the bearing member, and to cope with an increase in the capacity of the compression mechanism.

  As described above, according to the scroll compressor according to the present invention, with a simple configuration, the dimension shape of the balance weight is increased without reducing the area of the thrust bearing surface in the thrust plate and reducing the strength of the bearing member. Thus, it is possible to cope with an increase in the capacity of the compression mechanism.

It is a longitudinal cross-sectional view of the scroll compressor which concerns on embodiment of this invention. FIG. 2 is a longitudinal sectional view in the vicinity of a thrust plate and a balance weight showing a first embodiment of the present invention by enlarging a portion II in FIG. 1. It is a longitudinal cross-sectional view of thrust plate and balance weight vicinity which shows 2nd Embodiment of this invention.

Embodiments of the present invention will be described below with reference to the drawings.
FIG. 1 is a longitudinal sectional view of a scroll compressor according to an embodiment of the present invention. The scroll compressor 1 is an open type (a type in which a drive shaft projects outside) driven by an external drive source such as an engine, for example, and includes a front housing 3 and a rear housing 4 having a bottomed shape. Is provided with a cylindrical container-like housing 2 integrally connected by a plurality of bolts 5.

  A bearing member 6 is fixed to an opening end side of the front housing 3 inside the housing 2, and a drive shaft 9 is constituted by a radial bearing portion 6 </ b> A of the bearing member 6 and a rolling bearing 8 installed in the front housing 3. It is supported rotatably. The bearing member 6 includes a flange-shaped fixing portion 6B, and the fixing portion 6B is fastened and fixed to the front housing 3 by a plurality of bolts 7. One end of the drive shaft 9 protrudes outside through the front housing 3, and power from an external drive source such as an engine is input to the protruding portion via the pulley 10 and the electromagnetic clutch 11. ing.

  The pulley 10 is rotatably supported on the outer periphery of a flange member 13 fixed to the front end surface of the front housing 3 via a bolt 12 via a rolling bearing 14, and a coil assembly 15 of the electromagnetic clutch 11 is incorporated therein. It is a thing. Further, the armature assembly 16 of the electromagnetic clutch 11 is assembled to the external projecting end of the drive shaft 9 by a bolt 17 via the boss portion 16A so as to face the pulley 10. Further, a mechanical seal 18 for hermetically sealing the penetrating portion of the drive shaft 9 is installed on the inner peripheral side of the flange member 13.

  A compression mechanism 19 is incorporated on the rear housing 4 side inside the housing 2. In the compression mechanism 19, a fixed scroll 20 fixed inside the housing 2 and a turning scroll 21 facing the fixed scroll 20 are engaged with each other with a phase difference of 180 °. 22 is formed. Such a compression mechanism 19 itself is well known.

  The fixed scroll 20 is fastened and fixed to the bearing member 6 with a plurality of bolts 23, and a discharge cavity 26 is formed between the back surface of the end plate 20 </ b> A and the inner surface of the rear housing 4. A discharge port 24 that discharges compressed gas into the discharge cavity 26 and a discharge valve 25 that opens and closes the discharge port 24 are provided on the end plate 20 </ b> A of the fixed scroll 20. Further, the rear housing 4 is provided with a discharge port 27 for discharging the compressed gas discharged into the discharge cavity 26 to the outside, and a discharge pipe constituting a refrigeration cycle can be connected thereto.

  On the other hand, the orbiting scroll 21 has a cylindrical boss portion 28 formed at the center of the back surface of the end plate 21A, and a cylindrical drive bush 29 is rotatably fitted to the boss portion 28 via a bearing 30. Further, an eccentric pin 9A provided on the inner end side of the drive shaft 9 is rotatably fitted to the inner peripheral portion of the drive bush 29. For this reason, when the drive shaft 9 rotates, the orbiting scroll 21 is eccentrically driven by the eccentric pin 9A and the drive bush 29 that rotate eccentrically.

  Further, the orbiting scroll 21 is supported at its back surface by the annular thrust plate 32 fixed to the bearing member 6 by a plurality of bolts 31 and between the back surface of the end plate 21A and the bearing member 6. The rotation is prevented by a known rotation prevention mechanism 33 including an Oldham link or a pin ring interposed between the fixed scroll 20 and a revolving orbiting drive.

  A suction port 34 for connecting a suction pipe on the refrigeration cycle side is provided on the outer periphery on the front end side of the rear housing 4, and the low pressure gas sucked into the suction cavity 35 from the suction port 34 is compressed in the compression chamber 19. 22 is compressed by being sucked into 22 and discharged from a discharge port 27 through a discharge port 24 (discharge valve 25) and a discharge cavity 26.

  During operation of the compression mechanism 19, the orbiting scroll 21 is pressed in a direction away from the fixed scroll 20 (thrust direction) by the reaction force of the refrigerant compressed in the compression chamber 22. For this reason, the back surface of the end plate 21 </ b> A of the orbiting scroll 21 is pressed against the thrust bearing surface 32 </ b> S of the thrust plate 32, and the thrust force is received by the thrust plate 32. Lubricating oil is supplied between the end plate 21A and the thrust plate 32 from an oil supply passage (not shown), so that both the members 21A and 32 can smoothly slide relative to each other.

  As described above, the orbiting scroll 21 performs an eccentric orbiting motion with respect to the fixed scroll 20, so that if it remains as it is, rotational vibration is generated in the drive shaft 9 due to weight unbalance. In order to eliminate this weight imbalance, a main balance weight 41 and a sub balance weight 42 in which weights are arranged in a direction opposite to the eccentric direction of the orbiting scroll 21 are pivotally supported on the drive shaft 9.

  The main balance weight 41 is pivotally supported by the eccentric pin 9A of the drive shaft 9 via the drive bush 29, and is accommodated in a balance weight accommodation chamber 6C formed on the inner peripheral side of the bearing member 6 and swivels in the circumferential direction. To do. Further, the sub balance weight 42 is installed in the intermediate portion of the drive shaft 9 between the radial bearing portion 6A of the bearing member 6 and the rolling bearing 8, and in a balance weight storage chamber 6D formed on the outer peripheral side of the bearing member 6. It is housed and turns in the circumferential direction.

  That is, the main balance weight 41 and the sub balance weight 42 are provided adjacent to one and the other in the axial direction with respect to the bearing member 6. In other words, the layout is such that the bearing member 6 is sandwiched between the main balance weight 41 and the sub balance weight 42. By providing these balance weights 41 and 42, the centrifugal force accompanying the eccentric orbiting motion of the orbiting scroll 21 is canceled and the rotational vibration is suppressed.

[First Embodiment]
FIG. 2 is an enlarged longitudinal sectional view of the vicinity of the thrust plate 32 and the main / sub balance weights 41 and 42 showing the first embodiment of the present invention by enlarging the II part in FIG.
As described above, the main balance weight 41 is provided on the drive shaft 9 so as to be adjacent to the bearing member 6 in the axial direction, and has the inner peripheral overlap portion 41 </ b> A that overlaps the radially inner peripheral side of the bearing member 6. ing. The portion of the inner circumferential overlap portion 41A becomes a substantial weight portion and turns in the balance weight storage chamber 6C in the circumferential direction. A C-chamfered outer diameter reducing portion 41a is formed on the outer peripheral surface of the inner peripheral overlap portion 41A at the end on the thrust plate 32 side. The outer diameter reducing portion 41a has an outer conical surface shape whose outer diameter gradually decreases toward the thrust plate 32 side.

  On the other hand, the thrust plate 32 has a C chamfered inner diameter enlarged portion 32a formed on the inner diameter portion on the main balance weight 41 (inner peripheral overlap portion 41A) side. The inner diameter enlarged portion 32a has an inner conical surface shape whose inner diameter gradually increases toward the main balance weight 41 (41A). The outer diameter reduction part 41a of the main balance weight 41 (41A) and the inner diameter enlargement part 32a of the thrust plate 32 overlap in the radial direction and the axial direction, and face each other at a predetermined interval in parallel.

  The inclination angles of the conical surfaces of the outer diameter reducing portion 41 a and the inner diameter expanding portion 32 a are set to about 30 to 60 degrees with respect to the axis of the drive shaft 9. If the inclined surface of the inner diameter enlarged portion 32a is applied to the thrust bearing surface 32S, the inner diameter of the thrust bearing surface 32S is enlarged and the area of the thrust bearing surface 32S is reduced. Therefore, the inclined surface of the inner diameter enlarged portion 32a and the thrust bearing surface 32S It is preferable to set the inclination angle of the inner diameter enlarged portion 32a so as not to intersect.

  Since the thrust plate 32 is detachably fixed to the bearing member 6 with bolts 31 (see FIG. 1), the main balance weight 41 is moved away from the balance weight storage chamber 6C by loosening the bolts 31 and removing the thrust plate 32. Can be attached and detached.

  A C chamfered outer diameter reducing portion 41b is also formed at the end of the inner peripheral overlap portion 41A of the main balance weight 41 on the radial bearing portion 6A side. The outer diameter reducing portion 41b has an outer conical surface shape whose outer diameter gradually decreases in the axial direction toward the radial bearing portion 6A.

  On the other hand, the bearing member 6 has an inner diameter enlarged portion 6a. The inner diameter enlarged portion 6a has an inner conical surface shape whose inner diameter gradually increases toward the inner peripheral overlap portion 41A. The inner diameter enlarged portion 6a and the outer diameter reducing portion 41b of the inner peripheral overlap portion 41A overlap in the axial direction and the radial direction, and face each other at a predetermined interval.

  The sub balance weight 42 is provided on the opposite side of the main balance weight 41 with respect to the bearing member 6 in the axial direction so as to be adjacent to the axial direction, and overlaps with the outer peripheral side of the bearing member 6 in the radial direction. It has a portion 42A. The portion of the outer peripheral overlap portion 42A becomes a substantial weight portion and turns in the balance weight storage chamber 6D in the circumferential direction. The outer peripheral overlap portion 42A has an inner cone-shaped enlarged inner diameter portion 42a whose inner diameter gradually increases toward the fixed portion 6B side of the bearing member 6 in the axial direction.

  On the other hand, the bearing member 6 is formed with an outer diameter reducing portion 6b whose outer diameter gradually decreases toward the outer peripheral overlap portion 42A side of the subbalance weight 42. The outer diameter reducing portion 6b and the outer peripheral overlap portion 42A are formed. The inner diameter enlarged portion 42a overlaps in the axial direction and the radial direction, and is opposed in parallel with a predetermined interval.

The scroll compressor 1 configured as described above provides the following operational effects.
That is, in the scroll compressor 1, an outer diameter reducing portion 41a whose outer diameter decreases toward the thrust plate 32 side at the end portion of the main balance weight 41 (inner peripheral overlap portion 41A) on the thrust plate 32 side. Is formed on the inner diameter portion of the thrust plate 32 on the main balance weight 41 (41A) side, and an inner diameter enlarged portion 32a having an inner diameter that increases toward the main balance weight 41 side is formed. The outer diameter reduced portion 41a and the inner diameter enlarged portion 32a of the thrust plate 32 are overlapped in the radial direction and the axial direction.

  According to the above configuration, the inner diameter of the thrust plate 32 is increased from the thrust bearing surface 32S side toward the main balance weight 41 (41A) side by the inner diameter enlarged portion 32a. For this reason, the volume of the balance weight storage chamber 6C adjacent to the thrust plate 32 can be expanded in both the radial direction and the axial direction while keeping the area of the thrust bearing surface 32S at a predetermined size.

  As described above, since the outer diameter reducing portion 41 a of the main balance weight 41 overlaps the radial inner diameter portion 32 a of the thrust plate 32 in the radial direction and the axial direction, the axial dimension of the main balance weight 41 is set to the thrust plate 32. While extending to the side, the radial dimension can be increased.

  In the thrust plate 32, the area (radial width) of the thrust bearing surface 32S does not decrease as the outer diameter of the main balance weight 41 (41A) increases, and the orbiting scroll 21 (end plate 21A) and the thrust plate A sufficient contact area with 32 (thrust bearing surface 32S) can be secured.

  Therefore, the size and shape of the main balance weight 41 (41A) can be increased without reducing the area of the thrust bearing surface 32S in the thrust plate 32, and the capacity of the compression mechanism 19 can be increased.

  The outer diameter reducing portion 41a of the main balance weight 41 (41A) has an outer conical surface, and the inner diameter expanding portion 32a of the thrust plate 32 is opposed to the outer diameter reducing portion 41a in parallel with an interval therebetween. It is made into a shape. For this reason, the outer diameter reduced portion 41a of the main balance weight 41 is forced closer to the inner diameter enlarged portion 32a of the thrust plate 32 to increase the size and shape of the main balance weight 41 (41A) to cope with an increase in the capacity of the compression mechanism 19. can do.

  The inner peripheral overlap portion 41A of the main balance weight 41 overlaps the radially inner peripheral side of the bearing member 6, and the inner peripheral overlap portion 41A has an outer diameter in the axial direction toward the radial bearing portion 6A. The outer diameter reduced portion 41b is formed to gradually decrease, while the bearing member 6 is formed with an inner diameter enlarged portion 6a having an inner diameter gradually increasing toward the inner peripheral overlap portion 41A, and the inner diameter enlarged portion 6a and the outer diameter reduced portion are reduced. The portion 41b is overlapped in the axial direction and the radial direction.

  According to the above configuration, the outer diameter of the intermediate portion of the bearing member 6, that is, the outer diameter of the portion between the radial bearing portion 6A and the fixed portion 6B, is the inner diameter of the main balance weight 41 due to the slope shape of the inner diameter enlarged portion 6a. The diameter is increased in a conical cylinder shape toward the circumferential overlap portion 41A. For this reason, for example, as depicted by an imaginary line E in FIG. 2, the bearing member 6 has a larger portion than the case where the inner diameter enlarged portion 6 a is composed of a plane orthogonal to the axial direction and a cylindrical surface parallel to the axial direction. Thin parts do not occur. Therefore, the strength of the bearing member 6 is kept high, and the amount of bending can be reduced. Therefore, with a simple configuration, the size and shape of the main balance weight 41 (inner peripheral overlap portion 41A) can be increased without lowering the strength of the bearing member 6, and the capacity of the compression mechanism 19 can be increased.

  A sub-balance weight 42 separate from the main balance weight 41 is provided on the drive shaft 9 so as to be positioned on the opposite side of the main balance weight 41 and adjacent to the bearing member 6 in the axial direction. The subbalance weight 42 has an outer peripheral overlap portion 42A that overlaps the outer peripheral side of the bearing member 6 in the radial direction. The outer peripheral overlap portion 42A has an inner diameter toward the fixed portion 6B side of the bearing member 6 in the axial direction. An inner diameter enlarged portion 42a is formed so as to gradually increase. On the other hand, the bearing member 6 is formed with an outer diameter reduced portion 6b whose outer diameter gradually decreases toward the outer peripheral overlap portion 42A, and the outer diameter reduced portion 6b and the inner diameter enlarged portion 42a are formed in the axial direction and the diameter. It is stacked in the direction.

  According to the above configuration, the outer diameter of the intermediate portion of the bearing member 6 changes in a conical cylinder shape toward the outer peripheral overlap portion 42A side of the balance weight 42 due to the slope shape of the outer diameter reducing portion 6b. For this reason, for example, as illustrated by an imaginary line F in FIG. 2, the bearing member 6 is compared with a case where the portion of the outer diameter reducing portion 6 b is configured by a plane orthogonal to the axial direction and a cylindrical surface parallel to the axial direction. The thin part does not occur. Therefore, the strength of the bearing member 6 is kept high, and the amount of bending can be reduced. Therefore, with a simple configuration, the size and shape of the subbalance weight 42 (outer peripheral overlap portion 42A) can be increased without reducing the strength of the bearing member 6 to cope with an increase in the capacity of the compression mechanism 19.

[Second Embodiment]
FIG. 3 is a longitudinal sectional view of the vicinity of the thrust plate 32 and the main / sub balance weights 41 and 42 showing the second embodiment of the present invention. 3, the shape of the inner peripheral surface of the thrust plate 32 and the end shape of the main balance weight 41 (inner peripheral overlap portion 41A) on the thrust plate 32 side are the configurations of the first embodiment shown in FIG. Otherwise, the configuration is the same as that of FIG. For this reason, the same components as those in FIG.

  In the second embodiment, an outer diameter reduced portion 41c having an outer stepped cylindrical surface having at least one step is formed at the end of the main balance weight 41 (41A) on the thrust plate 32 side. . The thrust plate 32 is formed with an inner diameter enlarged portion 32b having an inner stepped cylindrical surface that meshes with the outer diameter reduced portion (41c) at an interval.

  Thereby, the main balance weight 41 (41A) in the first embodiment (FIG. 2) is similar to the combination of the outer conical outer diameter reducing portion 41a of the main balance weight 41 and the inner conical inner diameter expanding portion 32a of the thrust plate 32. The outer diameter reduced portion 41c of the balance weight 41 (41A) is brought close to the inner diameter enlarged portion 32b of the thrust plate 32 without difficulty, and the size and shape of the main balance weight 41 (41A) is increased in the radial direction and the axial direction. It is possible to cope with an increase in capacity.

  By forming the outer diameter reduced portion 41c and the inner diameter enlarged portion 32b in the shape of a stepped cylindrical surface, it is easier to process than the conical surface outer diameter reduced portion 41a and the inner diameter enlarged portion 32a in the first embodiment. it can. Note that two or more steps may be formed in the outer diameter reducing portion 41c and the inner diameter expanding portion 32b.

  In addition, this stepped cylindrical surface configuration is configured such that the inner diameter enlarged portion 6a of the bearing member 6 and the outer diameter reduced portion 41b of the main balance weight 41 (41A) face each other, or the outer diameter reduced portion 6b of the bearing member 6. You may apply to the opposing part with the internal diameter expansion part 42a of the subbalance weight 42 (42A).

It should be noted that the present invention is not limited to the configuration of the above-described embodiment, and can be appropriately changed or improved. Embodiments with such changes and improvements are also included in the scope of the right of the present invention. And
For example, in the above-described embodiment, the example in which the present invention is applied to the open scroll compressor 1 in which the drive shaft 9 is rotationally driven by external power has been described. However, the sealed type in which the drive shaft is rotationally driven by a built-in electric motor. The present invention can also be applied to other scroll compressors.

1 Scroll compressor 2 Housing 6 Bearing member (main bearing)
6A Radial bearing portion 6B Bearing member fixed portion 6a Inner diameter enlarged portion 6b Outer diameter reduced portion 9 Drive shaft 20 Fixed scroll 21 Orbiting scroll 21A Orbiting scroll end plate 32 Thrust plate 32S Thrust bearing surfaces 32a, 32b Inner diameter enlarged portion 41 Main balance Weight 41A Inner circumference overlap portions 41a, 41b, 41c Outer diameter reduction portion 42 Subbalance weight 42A Outer circumference overlap portion 42a Inner diameter enlargement portion

Claims (5)

A fixed scroll fixed inside the housing;
A orbiting scroll that meshes against the fixed scroll; and
A drive shaft for eccentrically orbiting the orbiting scroll;
A bearing member provided inside the housing and supporting the drive shaft;
An annular thrust plate that is installed inside the housing and whose thrust bearing surface is in contact with the back of the end plate of the orbiting scroll and receives the thrust force acting on the orbiting scroll;
A main balance weight that is provided on the drive shaft and is adjacent to the thrust plate in the axial direction, and cancels centrifugal force associated with the eccentric orbiting motion of the orbiting scroll;
With
The main balance weight has an outer diameter reducing portion whose outer diameter gradually decreases toward the thrust plate side at an end portion of the thrust plate side,
The thrust plate has an inner diameter enlarged portion whose inner diameter gradually increases toward the main balance weight side on the main balance weight side of the inner diameter portion,
A scroll compressor in which the outer diameter reduced portion and the inner diameter enlarged portion overlap in a radial direction and an axial direction.   2. The scroll compressor according to claim 1, wherein the outer diameter reducing portion has an outer conical surface shape, and the inner diameter expanding portion has an inner conical surface shape facing the outer diameter reducing portion with a space therebetween in parallel.   The outer diameter reducing portion has an outer stepped cylindrical surface shape having at least one step portion, and the inner diameter expanding portion has an inner stepped cylindrical surface shape that meshes with the outer diameter reducing portion at an interval. Item 2. The scroll compressor according to Item 1. The main balance weight is provided so as to be adjacent to the bearing member in the axial direction, and has an inner circumferential overlap portion that overlaps the radially inner circumferential side of the bearing member,
The inner circumferential overlap portion has an outer diameter reduction portion in which the outer diameter gradually decreases toward the radial bearing portion side of the bearing member in the axial direction,
The bearing member has an inner diameter enlarged portion in which an inner diameter gradually increases toward the inner circumferential overlap portion side,
The scroll compressor according to any one of claims 1 to 3, wherein the outer diameter reduced portion and the inner diameter enlarged portion overlap in an axial direction and a radial direction. Further comprising a sub balance weight separate from the main balance weight,
The sub-balance weight is provided on the opposite side of the main balance weight with respect to the bearing member so as to be adjacent to the axial direction, and has an outer peripheral overlap portion that overlaps the radial outer peripheral side of the bearing member. And
The outer peripheral overlap portion has an inner diameter enlarged portion whose inner diameter gradually increases in the axial direction toward the fixed portion side of the bearing member,
The bearing member has an outer diameter reducing portion in which an outer diameter gradually decreases toward the outer peripheral overlap portion side,
The scroll compressor according to any one of claims 1 to 4, wherein the inner diameter enlarged portion and the outer diameter reduced portion overlap in an axial direction and a radial direction.

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