WO2020230773A1

WO2020230773A1 - Scroll compressor

Info

Publication number: WO2020230773A1
Application number: PCT/JP2020/018912
Authority: WO
Inventors: 飯塚　二郎; 淳夫手島
Original assignee: サンデン・オートモーティブコンポーネント株式会社
Priority date: 2019-05-16
Filing date: 2020-05-12
Publication date: 2020-11-19

Abstract

[Problem] To provide a scroll compressor with which effective miniaturization can be achieved. [Solution] A scroll compressor 100 comprises, in a housing 10, the following: a fixed scroll 2 and a moving scroll 3; a thrust receiving part 24 that receives a thrust force of the moving scroll 3; and a drive shaft 21. The thrust receiving part 24 includes a through-hole 24a1 that: provides a partition between a first region V1 in which the drive shaft 21 extends within the housing 10 and into which fluid is guided from outside, and a second region V2 in which the fixed scroll 2 and the moving scroll 3 are arranged; and establishes communication between the first region V1 and a fluid intake region H1 close to the outer spiral end of wraps 2b, 3b in the second region V2. An impeller 27, which is attached to the drive shaft 21, rotates integrally with the drive shaft 21 and sends the fluid in the first region V1 toward the thrust receiving part 24.

Description

Scroll compressor

The present invention relates to a scroll type compressor that has fixed scrolls and movable scrolls that are meshed with each other and compresses a fluid by changing the volume of a closed space formed by these.

The scroll type compressor is equipped with a fixed scroll and a movable scroll that are meshed with each other and a drive mechanism for transmitting a revolving driving force around the axis of the fixed scroll to the movable scroll. A closed space whose volume changes with revolution is formed between the two, and the compressible fluid is compressed and discharged by this closed space.

As a scroll type compressor of this type, for example, the one described in Patent Document 1 is generally known. The sealed case 4 as a housing in the scroll type compressor described in Patent Document 1 is divided into a front block 2 and a rear block 3. A drive shaft (specifically, a rotation shaft 6 and an eccentric shaft 12) forming a part of the drive mechanism extends in the front block 2, and a swing scroll as a movable scroll is in the rear block 3. A member 20 (hereinafter referred to as a movable scroll) and a fixed scroll member 30 (hereinafter referred to as a fixed scroll) as a fixed scroll are provided. This scroll type compressor is a compressor incorporated in the refrigerant circuit of the vehicle air conditioner, compresses and discharges the refrigerant (fluid) guided from the low pressure side of the refrigerant circuit, and is a refrigerant suction port 41 in the rear block 3. Is formed. The refrigerant suction port 41 communicates with a suction space 43 formed near the outer end of the spiral of the spiral wrap of the movable scroll and the fixed scroll. The refrigerant guided to the suction space 43 is taken into the compression chamber 40 as a closed space between the movable scroll and the fixed scroll, compressed, and discharged to the high pressure side of the refrigerant circuit.

Japanese Unexamined Patent Publication No. 11-44295

Here, this type of scroll compressor is often incorporated into a device such as a refrigerant circuit of a vehicle air conditioner like the scroll compressor described in Patent Document 1 to form a part of the device. Therefore, in this type of scroll type compressor, the installation space in the apparatus may be restricted, and some measures for miniaturization are required.

The present invention has been made by paying attention to the above problems, and an object of the present invention is to provide a scroll type compressor capable of effectively reducing the size.

According to one aspect of the present invention, the fixed scroll and the movable scroll having spiral wraps and meshing with each other, the thrust receiving portion provided on the back side of the movable scroll and receiving the thrust force of the movable scroll, and the movable scroll A scroll type compressor is provided in which a drive shaft forming a part of a drive mechanism for transmitting a revolution drive force is provided in a housing. In this scroll type compressor, the movable scroll revolves to form a closed space whose volume changes with the revolution between the movable scroll and the fixed scroll, and the compressible fluid is compressed and discharged by this closed space. The thrust receiving portion divides the inside of the housing into a first region and a second region. The first region is a space in which the drive shaft extends and the fluid is guided from the outside, and the second region is a space in which the fixed scroll and the movable scroll are arranged. The thrust receiving portion has a communication hole that communicates the fluid intake region near the spiral outer end portion of the lap of the fixed scroll and the movable scroll in the first region and the second region. An impeller that rotates integrally with the drive shaft and sends the fluid in the first region to the thrust receiving portion side is attached to the drive shaft.

In the scroll type compressor with one side surface, the space inside the housing is arranged by the thrust receiving portion, the first region in which the drive shaft extends and the fluid is guided from the outside, and the fixed scroll and the movable scroll. It is divided into regions, and the first region and the fluid intake region near the outer end of the spiral of the wrap are communicated with each other by a communication hole in the thrust receiving portion. Then, the fluid in the first region is sent out to the thrust receiving portion side by the impeller attached to the drive shaft in the first region. Therefore, the fluid in the first region is pushed into the fluid intake region through the communication hole by the impeller and is taken into the fluid intake region. That is, the blower composed of the impeller, the drive shaft, and the housing has a function as a so-called supercharger. Then, the fluid taken into the fluid intake region is compressed and discharged in the closed space between the fixed scroll and the movable scroll via the outer end of the spiral of the wrap. Therefore, in the scroll type compressor with one side surface, the fluid in the first region can be pushed into the fluid intake region to increase the pressure, so that the amount of fluid flowing into the closed space from the fluid intake region is increased. It is possible to increase the amount of the fluid as it is, and to increase the amount of the compressed fluid to be discharged. Therefore, when the capacity required for the compressor (for example, the amount of discharged gas) is the same, the volume of the enclosed space can be made smaller than before, so that the compressor can be made smaller than before. Further, when the size of the compressor may be the same as the conventional one, the capacity of the compressor can be increased while maintaining the size of the compressor.

In this way, it is possible to provide a scroll type compressor that can be miniaturized.

It is the schematic sectional drawing of the scroll type compressor in one Embodiment of this invention. It is sectional drawing of the arrow AA shown in FIG. It is a front view of the drive shaft of a scroll type compressor. It is a front view of the rocking member of a scroll type compressor. It is a front view of the thrust receiving part of a scroll type compressor. It is a rear view of the movable scroll of a scroll type compressor. It is a front view of the impeller of a scroll type compressor. FIG. 7 is a cross-sectional view taken along the line BB shown in FIG. FIG. 7 is a cross-sectional view taken along the line CC shown in FIG. It is schematic cross-sectional view for demonstrating the modification of the scroll type compressor. It is the schematic sectional drawing for demonstrating another modification of a scroll type compressor. It is a front view of the impeller in the above-mentioned another modification.

Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings.
FIG. 1 is a schematic cross-sectional view showing the overall configuration of the scroll type compressor according to the present embodiment, and FIG. 2 is a cross-sectional view taken along the line AA shown in FIG. 3 to 6 are component views of the scroll compressor, FIG. 3 is a front view of the drive shaft, FIG. 4 is a front view of the swing member, FIG. 5 is a front view of the thrust receiving portion, and FIG. It is a rear view of a scroll.

The scroll type compressor 100 in the present embodiment is a compressible fluid incorporated in a refrigerant circuit of a vehicle air conditioner capable of performing, for example, cooling operation and heating operation by a heat pump, and sucked from the low pressure side of the refrigerant circuit. A compressor that compresses and discharges the refrigerant. The scroll type compressor 100 includes a scroll unit 1, a housing 10, and a drive mechanism 20 for transmitting a revolution driving force to the scroll unit 1. The scroll unit 1 and the drive mechanism 20 are provided in the housing 10. In the present embodiment, the scroll type compressor 100 also includes an electric motor 30 which is a drive source of the scroll unit 1 in the housing 10. Further, the scroll type compressor 100 includes an inverter 40 for controlling the drive of the electric motor 30 in the housing 10, and is a so-called inverter-integrated electric compressor.

As shown in FIG. 1, the scroll unit 1 has a fixed scroll 2 and a movable scroll 3 that are meshed with each other. In the scroll type compressor 100, the movable scroll 3 revolves around the axis X'of the fixed scroll 2 while being in contact with the fixed scroll 2, and the volume of the movable scroll 3 changes with the fixed scroll 2 in accordance with the revolution. Is formed, and the refrigerant is compressed and discharged by the closed space S. For example, the fixed scroll 2 and the movable scroll 3 are made of an aluminum alloy.

Specifically, the fixed scroll 2 has a first bottom plate 2a formed in a disk shape and having a discharge hole 2a1 opened in the center thereof, and a spiral first plate erected on one end surface of the first bottom plate 2a. It has a wrap 2b. The movable scroll 3 has a disk-shaped second bottom plate 3a having one end surface facing the one end surface of the first bottom plate 2a, and a spiral second wrap 3b erected on one end surface of the second bottom plate 3a. .. Further, the first bottom plate 2a of the fixed scroll 2 has a larger diameter than the second bottom plate 3a of the movable scroll 3. In the present embodiment, the first lap 2b corresponds to the "lap" of the "fixed scroll" according to the present invention, and the second lap 3b corresponds to the "lap" of the "movable scroll" according to the present invention.

The fixed scroll 2 and the movable scroll 3 are arranged so that the first lap 2b and the second lap 3b mesh with each other. Specifically, the fixed scroll 2 and the movable scroll 3 have the side wall of the first lap 2b and the second lap in a state where the circumferential angle of the first lap 2b and the circumferential angle of the second lap 3b are deviated from each other. The side walls of 3b are arranged so as to partially contact each other. As a result, a plurality of crescent-shaped sealed spaces S are formed between the first lap 2b and the second lap 3b. Further, the fixed scroll 2 and the movable scroll 3 have a gap between the protruding end of the first wrap 2b and the second bottom plate 3a, and between the protruding end of the second wrap 3b and the first bottom plate 2a. It is arranged so as to have a gap. In the present embodiment, the tip seal member 4 is fitted into the groove portion formed at the protruding end portion of the first wrap 2b and the groove portion formed at the protruding end portion of the second wrap 3b, respectively. The chip seal member 4 appropriately maintains the airtightness of the sealed space S, and maintains the compression performance of the refrigerant in the scroll type compressor 100.

More specifically, the fixed scroll 2 has a cylindrical cylindrical portion 2c that is erected on an outer edge portion on one end surface of the first bottom plate 2a on the lap side. The cylindrical portion 2c has an outer diameter that matches the inner diameter of the opening on one end side (upper side in FIG. 1) of the center housing 11 described later in the housing 10. The fixed scroll 2 is fitted in the center housing 11 so that the first wrap 2b and the cylindrical portion 2c face the inside of the center housing 11 and close the opening on one end side of the center housing 11.

The movable scroll 3 is fitted inside the cylindrical portion 2c through the opening of the cylindrical portion 2c of the fixed scroll 2 with the second wrap 3b facing the first bottom plate 2a side. In this state, the fluid intake region H1 is formed in the vicinity of the spiral outer end portion of the first lap 2b and the second lap 3b in the scroll unit 1. The fluid intake region H1 is open at the end surface of the scroll unit 1 on the second bottom plate 3a side.

The movable scroll 3 is configured to revolve around the axis X'of the fixed scroll 2 in a state where its rotation is prevented via the drive mechanism 20. As a result, the scroll unit 1 gradually reduces the volume of the closed space S while moving the closed space S to the central portion. As a result, the scroll unit 1 compresses the refrigerant flowing into the closed space S from the fluid intake region H1 in the closed space S.

The housing 10 has a center housing 11, a front housing 12, and a rear housing 13. Then, these (11, 12, 13) are integrally fastened by a fastening member such as a bolt 14, so that the housing 10 of the scroll type compressor 100 is configured. The housing 10 is made of, for example, an aluminum alloy.

The space inside the housing 10 is divided into a first region V1 and a second region V2 by a thrust receiving portion 24 described later. A drive shaft 21, which will be described later, forms a part of the drive mechanism 20 extends in the first region V1, and a refrigerant is guided from the outside (a portion on the low voltage side of the refrigerant circuit) via the suction port P1. The scroll unit 1 is arranged in the second region V2. Further, in the present embodiment, the electric motor 30 is also provided in the first region V1.

The center housing 11 has a substantially cylindrical peripheral wall portion 11a having a first region V1 and a second region V2 inside, and an annular protrusion projecting inward along an inner peripheral surface intermediate in the longitudinal direction of the peripheral wall portion 11a. It has a setting portion 11b. The scroll unit 1, the drive mechanism 20, and the electric motor 30 are mainly housed in the center housing 11. The end surface of the outer edge portion 13a of the rear housing 13 is in contact with one end of the peripheral wall portion 11a. Further, the opening on the other end side (lower side in FIG. 1) of the peripheral wall portion 11a is closed by the box bottom portion 12a described later of the front housing 12.

The above-mentioned suction port P1 is not particularly limited, but is formed at a portion of the peripheral wall portion 11a corresponding to the first region V1. As described above, the housing 10 (the peripheral wall portion 11a in the present embodiment) is formed with the suction port P1 for guiding the refrigerant (fluid) into the housing 10 from the outside. Specifically, the suction port P1 is provided at a portion of the peripheral wall portion 11a corresponding to the end portion of the electric motor 30 opposite to the thrust receiving portion 24. In the present embodiment, the opening end P11 on the first region V1 side (that is, the internal space side of the housing 10) of the suction port P1 is opened in the end region V11 opposite to the thrust receiving portion 24 in the first region V1. ing. The surface of the front housing 12 on the first region V1 side of the box bottom portion 12a, which will be described later, is exposed in this end region V11. Then, the refrigerant from the low pressure side of the refrigerant circuit is sucked into the housing 10 (center housing 11) through the suction port P1. That is, the suction port P1 is open to the first region V1, and the first region V1 functions as a suction chamber. In the present embodiment, the electric motor 30 is cooled by circulating the refrigerant from the suction port P1 around the electric motor 30 and in the gap in the electric motor 30 in the first region V1. ing. Then, in FIG. 1, the space on the upper side (thrust receiving portion 24 side) of the electric motor 30 in the first region V1 is the space on the lower side (opposite side of the thrust receiving portion 24) of the electric motor 30 in the first region V1. That is, it communicates with the above-mentioned end region V11) and constitutes one first region (suction chamber) V1 together with the space under the electric motor 30. Further, an appropriate amount of lubricating oil is stored in the first region V1 for lubrication of sliding portions such as the drive mechanism 20. Therefore, in the first region V1, the refrigerant flows as a mixed fluid with the lubricating oil.

The end surface 11b1 on the rear housing 13 side of the projecting portion 11b is formed as an annular surface orthogonal to the rotation axis X of the drive shaft 21 (detailed later described later) of the drive mechanism 20. The end surface of the outer edge portion of the thrust receiving portion 24 of the drive mechanism 20 is brought into contact with the end surface 11b1. Since the fixed scroll 2 is sandwiched between the thrust receiving portion 24 and the rear housing 13, the fixed scroll 2 is fixed in the center housing 11 together with the thrust receiving portion 24.

The front housing 12 is formed in a box shape having one end opened as a whole, and is projected from the box bottom portion 12a that closes the opening on the other end side of the peripheral wall portion 11a of the center housing 11 and the outer edge portion of the box bottom portion 12a. It has a side wall portion 12b and houses the inverter 40 inside. In other words, the box bottom portion 12a closes the opening on the first region V1 side in the peripheral wall portion 11a of the center housing 11. At the center of the surface of the box bottom 12a on the first region V1 side, a tubular support portion 12a1 for holding a front bearing 16 that rotatably supports the end portion (lower end portion in FIG. 1) of the spindle 21a is provided as a center housing. It is projected toward the inside of 11. The inverter 40 is fixed to the surface of the box bottom 12a opposite to the first region V1. Further, the opening on one end side of the front housing 12 is closed by the inverter cover 15 formed in a plate shape. The inverter cover 15 is fastened to the side wall portion 12b of the front housing 12 by bolts 14. As described above, in the present embodiment, the housing 10 has a tubular peripheral wall portion 11a having a first region V1 and a second region V2 inside, and a box bottom portion 12a that closes the opening on the first region V1 side in the peripheral wall portion 11a. And have. In the present embodiment, the box bottom portion 12a corresponds to the "bottom wall portion" according to the present invention.

The rear housing 13 is formed in a substantially disk shape having an outer diameter matching the outer diameter of the peripheral wall portion 11a of the center housing 11, and the central portion 13b thereof is formed so as to bulge outward. The outer edge portion 13a of the rear housing 13 is fastened to one end of the peripheral wall portion 11a by an appropriate number of fastening members such as bolts 14.

Further, the radial inner portion 13a1 of the outer edge portion 13a of the rear housing 13 projects radially inward from the inner peripheral surface of the peripheral wall portion 11a of the center housing 11. When the end surface of the inner portion 13a1 comes into contact with the outer edge portion of the other end surface (the end surface on the side opposite to the end surface on the wrap 2b side) of the first bottom plate 2a of the fixed scroll 2, the fixed scroll 2 and the thrust receiving portion 24 It is sandwiched between the outer edge portion 13a (specifically, the inner portion 13a1) of the rear housing 13. The refrigerant discharge chamber H2 is partitioned by the bulging central portion 13b of the rear housing 13 and the first bottom plate 2a. A seal member 17 is provided at a contact portion (the outer edge portion) of the fixed scroll 2 with the inner portion 13a1 of the rear housing 13. The discharge chamber H2 communicates with the closed space S via the discharge hole 2a1 formed in the central portion of the first bottom plate 2a. A valve 18 is provided in the discharge chamber H2 so as to cover the opening of the discharge hole 2a1. On the other hand, the valve 18 is a check valve that allows the refrigerant to flow from the closed space S to the discharge chamber H2 and prevents the refrigerant from flowing back from the discharge chamber H2 to the closed space S. In the discharge chamber H2, the refrigerant compressed in the closed space S is discharged through the discharge holes 2a1 and the one-side valve 18. The compressed refrigerant in the discharge chamber H2 is discharged to the high pressure side of the refrigerant circuit through a discharge port (not shown) formed in the rear housing 13.

The drive mechanism 20 is a mechanism for transmitting the revolution driving force around the axis X'of the fixed scroll 2 to the movable scroll 3. In the present embodiment, the drive mechanism 20 also has a function of preventing the movable scroll 3 from rotating.

As shown in FIGS. 1 and 2, in the present embodiment, the drive mechanism 20 includes a drive shaft 21, a swivel bearing 22, an annular swing member 23, a thrust receiving portion 24, and a rotation prevention mechanism portion 25. , A rear bearing 26 and a connecting pin 25a.

As shown in FIGS. 1 to 3, the drive shaft 21 has a main shaft 21a and an eccentric shaft 21b. The spindle 21a is rotationally driven around the rotation axis X. The rotation axis X of the spindle 21a is aligned with the axis X'of the fixed scroll 2. The eccentric shaft 21b is provided at one end of the main shaft 21a in the axial direction so as to be eccentric with respect to the rotation axis X. The drive shaft 21 is made of, for example, a steel material.

An impeller 27 is attached to the drive shaft 21 that rotates integrally with the drive shaft 21 and sends out the refrigerant in the first region V1 to the thrust receiving portion 24 side. That is, the blower is composed of the casing composed of the center housing 11 forming the first region V1, the drive shaft 21, and the impeller 27. Further, in the present embodiment, a counterweight 28 for ensuring a weight balance with respect to the movable scroll 3 is provided integrally with the impeller 27. The impeller 27 and the counterweight 28 will be described in detail later.

At one end of the main shaft 21a, a flange-shaped flange portion 21a1 is provided integrally with the eccentric shaft 21b. The other end of the spindle 21a is reduced in diameter and is rotatably supported by a front bearing 16 fitted to the support 12a1.

Specifically, the eccentric shaft 21b has a circular cross section centered on the axis eccentric with respect to the rotation axis X of the main shaft 21a, and extends toward the scroll unit 1 side.

In the present embodiment, the eccentric shaft 21b is formed with a circular hole 21b1 concentric with the rotation axis X. That is, the center of the outer diameter of the eccentric shaft 21b is located on the axis eccentric with respect to the rotation axis X of the spindle 21a, but the center of the inner diameter of the eccentric shaft 21b is on the rotation axis X of the spindle 21a. positioned. In other words, the eccentric shaft 21b is formed in a tubular shape, and the center of the outer diameter of the cylinder is the inner diameter of the cylinder so that the first lap 2b of the fixed scroll 2 and the second lap 3b of the movable scroll 3 slide appropriately. Is eccentric with respect to the center of.

In the present embodiment, the eccentric shaft 21b is formed separately from the main shaft 21a. Specifically, the circular hole 21b1 of the eccentric shaft 21b has a hole diameter that matches the outer diameter of the main shaft 21a and penetrates the eccentric shaft 21b. The flange portion 21a1 is formed in an eccentric flange shape on the outer circumference of one end of the eccentric shaft 21b. The eccentric shaft 21b is fixed to one end of the main shaft 21a by press-fitting one end of the main shaft 21a into the circular hole 21b1 of the eccentric shaft 21b while leaving the accommodation area of the rear bearing 26. That is, a circular recess is formed at one end (eccentric shaft side end) of the drive shaft 21 by the hole wall surface of the circular hole 21b1 and the end surface of one end of the main shaft 21a. The convex portion 24b of the thrust receiving portion 24, which will be described later, is inserted into the circular concave portion.

The swivel bearing 22 is a bearing mounted on the outer peripheral surface of the eccentric shaft 21b, and is, for example, a cylindrical slide bearing. The swivel bearing 22 has a height substantially matching the height of the flange portion 21a1 of the eccentric shaft 21b from the flange surface.

The swing member 23 is mounted on the outer peripheral surface of the swivel bearing 22. The rocking member 23 is formed in a disk shape having a thickness corresponding to the height of the swivel bearing 22, and is made of, for example, an aluminum alloy material. A swivel bearing mounting hole 23a having an inner diameter matching the outer diameter of the swivel bearing 22 is opened in the central portion of the swing member 23. The swivel bearing 22 is fitted into the swivel bearing mounting hole 23a.

As shown in FIG. 4, connecting pins 25a, which will be described later, are inserted into a plurality of portions (6 locations in FIGS. 2 and 4) at equal intervals in the circumferential direction at the outer edge portion of the rocking member 23. A hole (hereinafter referred to as an insertion hole) 23b is penetrated. The rocking member 23 is formed so that the region between the insertion holes 23b at the outer edge thereof is recessed inward in the radial direction. As a result, the weight of the swing member 23 is reduced. Further, the recess of the outer edge portion of the swing member 23 is formed from the first region V1 to the first lap 2b of the scroll unit 1 together with the communication hole 24a1 which is at least a part of the through hole 24a of the thrust receiving portion 24 described later. It functions as a refrigerant introduction passage for introducing a refrigerant (specifically, a mixed fluid of a refrigerant and a lubricating oil) into a fluid intake region H1 formed near the outer end of the spiral of the second wrap 3b. Therefore, the dent on the outer edge of the rocking member 23 sufficiently secures the refrigerant introduction passage, and the pressure loss of the refrigerant introduction passage can be easily reduced. A swivel bearing 22 is mounted between the wall surface of the swivel bearing mounting hole 23a of the swing member 23 and the outer peripheral surface of the eccentric shaft 21b. As a result, the swing member 23 is rotatably attached to the eccentric shaft 21b via the swivel bearing 22 around the axis of the eccentric shaft 21b (that is, the axis eccentric with respect to the rotation axis X of the spindle 21a). Has been done.

As shown in FIG. 1, the thrust receiving portion 24 is provided on the back side of the movable scroll 3 and receives the thrust force of the movable scroll 3. In the present embodiment, the thrust receiving portion 24 is provided between the second bottom plate 3a of the movable scroll 3 and the swing member 23. In other words, the rocking member 23 is arranged so as to sandwich the thrust receiving portion 24 between the rocking member 23 and the second bottom plate 3a of the movable scroll 3.

In the present embodiment, the thrust receiving portion 24 is formed separately from the housing 10. Specifically, the thrust receiving portion 24 is appropriately made of, for example, a steel material having better wear resistance than the material (for example, an aluminum alloy) used for the movable scroll 3, the swing member 23, and the housing 10. It consists of members. The thrust receiving portion 24 is formed in a substantially disk shape having an outer diameter matching the inner diameter of the opening on one end side (upper side in FIG. 1) of the center housing 11. The end surface of the outer edge portion of the thrust receiving portion 24 is in contact with the end surface 11b1 of the projecting portion 11b of the center housing 11 as described above. The thrust receiving portion 24 is fixed in the center housing 11 by, for example, its outer edge portion being sandwiched between the tip surface of the cylindrical portion 2c of the fixed scroll 2 and the end surface 11b1 of the projecting portion 11b. The angular position of the thrust receiving portion 24 with respect to the fixed scroll 2 in the circumferential direction is determined by an appropriate positioning means such as a pin and a pin hole (not shown). As described above, the space inside the housing 10 (specifically, the peripheral wall portion 11a of the center housing 11) is divided into a first region V1 and a second region V2 by the thrust receiving portion 24. Further, in the drive shaft 21, the amount of play in the rotation axis X direction is regulated by the thrust receiving portion 24 and the front bearing 16.

As shown in FIGS. 1 and 5, a plurality of through holes 24a penetrating the outer edge portion are formed in the outer edge portion of the thrust receiving portion 24. In the present embodiment, the through holes 24a are opened in a circular shape, and are opened at a plurality of (six locations in FIG. 5) portions of the outer edge portion of the thrust receiving portion 24 that are spaced apart at equal intervals in the circumferential direction.

In the present embodiment, a columnar convex portion 24b is projected from the central portion of the end surface of the thrust receiving portion 24 on the swing member side. The convex portion 24b has an outer diameter that matches the inner diameter of the rear bearing 26. The protruding height of the convex portion 24b is substantially matched to the height of the swivel bearing 22. The rear bearing 26 is mounted on the outer peripheral surface of the convex portion 24b.

As shown in FIG. 1, the seal member 19 is arranged on the other end surface (that is, the end surface on the thrust receiving portion side) which is the back surface of the second bottom plate 3a of the movable scroll 3. The annular sealing member 19 maintains the airtightness of the back pressure chamber H3 partitioned between the back surface of the second bottom plate 3a and the movable scroll side end surface of the thrust receiving portion 24. The back pressure chamber H3 has a gap height (for example, less than 0.5 mm) in the rotation axis X direction of the spindle 21a determined by the crushing allowance of the seal member 19, and in FIG. 1, this gap height is It has not appeared. A communication passage 3d that connects the closed space S and the back pressure chamber H3 is opened in the central portion of the second bottom plate 3a of the movable scroll 3. Further, the back pressure chamber H3 is blocked from communicating with a region whose pressure is lower than the pressure in the back pressure chamber H3. Therefore, even if a part of the high-pressure refrigerant obtained by the compression operation is supplied to the back pressure chamber H3 via the communication passage 3d for back pressure formation, the refrigerant is in a region lower than the pressure in the back pressure chamber H3. It will not be washed away. As a result, energy loss can be reduced.

A groove 3e for attaching the seal member 19 is formed on the back surface of the second bottom plate 3a of the movable scroll 3. As shown in FIGS. 1 and 6, when the movable scroll 3 revolves around the axis X'of the fixed scroll 2, the seal member 19 does not enter the regions of the plurality of through holes 24a in the thrust receiving portion 24. As described above, the formation path of the groove portion 3e is defined.

Further, the thrust receiving portion 24 has a communication hole 24a1 that communicates the first lap 2b and the fluid intake region H1 near the outer end of the spiral of the second lap 3b in the first region V1 and the second region V2. There is. The opening of the communication hole 24a1 is formed in the thrust receiving portion 24 so as to face the opened portion of the fluid intake region H1 at the end surface of the scroll unit 1 on the second bottom plate 3a side. In the present embodiment, the communication hole 24a1 is composed of at least a part of a plurality of through holes 24a (for example, one through hole 24a), and functions as a refrigerant introduction passage for introducing the refrigerant into the fluid intake region H1.

As shown in FIGS. 1 and 6, a plurality of holes 3c are opened in the outer edge portion of the second bottom plate 3a of the movable scroll 3. The hole 3c of the movable scroll 3 is opened at the same position as the opening position of the insertion hole 23b opened in the swing member 23.

The rotation prevention mechanism unit 25 is a mechanism for preventing the rotation of the movable scroll 3. In the present embodiment, the rotation prevention mechanism portion 25 penetrates the plurality of through holes 24a described above that penetrate the outer edge portion of the thrust receiving portion 24, and penetrates the through holes 24a, and also penetrates the outer edge portion of the swing member 23 and the movable scroll 3. It is composed of a connecting pin 25a that connects the second bottom plate 3a to the outer edge portion. The connecting pin 25a prevents the movable scroll 3 from rotating and transmits the revolution driving force of the movable scroll 3 to the movable scroll 3 by sliding the intermediate portion thereof against the hole wall surface of the through hole 24a. That is, in the present embodiment, the connecting pin 25a has both a function of transmitting the revolution driving force and a function of preventing the rotation of the movable scroll 3. The insertion hole 23b in the swing member 23 and the hole 3c in the movable scroll 3 are formed at positions corresponding to the through holes 24a. The inner diameter of the through hole 24a is larger than the inner diameter of the insertion hole 23b and the hole 3c, and is determined according to, for example, the revolution turning radius required by the movable scroll 3. The connecting pin 25a is made of a steel material like the thrust receiving portion 24, and is formed in a columnar shape having a diameter smaller than that of the through hole 24a, for example. In this way, the rotation prevention mechanism portion 25 for preventing the rotation of the movable scroll 3 is configured by the intermediate portion of the connecting pin 25a sliding in contact with the hole wall surface of the through hole 24a. Further, the drive mechanism 20 including the rotation prevention mechanism unit 25 has a connecting pin 25a, and transmits the revolution driving force to the movable scroll 3 via the connecting pin 25a.

The rear bearing 26 is fitted between the outer peripheral surface of the convex portion 24b of the thrust receiving portion 24 and the inner peripheral surface of the circular hole 21b1 of the eccentric shaft 21b, and rotates the eccentric shaft 21b which is one end of the drive shaft 21. It is a bearing that rotatably supports around X. In the rear bearing 26, for example, the outer peripheral surface of the rear bearing 26 slides with respect to the inner peripheral surface of the circular hole 21b1, and the inner peripheral surface of the rear bearing 26 slides with respect to the outer peripheral surface of the convex portion 24b. , It is fitted between the outer peripheral surface of the convex portion 24b and the inner peripheral surface of the circular hole 21b1. The rear bearing 26 is made of, for example, a cylindrical slide bearing similar to the swivel bearing 22. As a result, one end portion (eccentric shaft side end portion) of the drive shaft 21 is rotatably supported by the rear bearing 26, and the other end portion (inverter side end portion) of the drive shaft 21 is fitted into the support portion 12a1. It is rotatably supported by the front bearing 16 and both ends of the drive shaft 21 are rotatably supported in the housing 10. Further, one end of the drive shaft 21 is rotatably supported via the convex portion 24b of the thrust receiving portion 24. That is, in the present embodiment, the eccentric shaft 21b (in other words, the end of the drive shaft 21 on the thrust receiving portion 24 side), which is one end portion of the drive shaft 21, can be rotated around the rotation axis X by the thrust receiving portion 24. Is supported by.

The electric motor 30 is a drive source for the scroll unit 1 and generates a rotational driving force for the drive shaft 21 (specifically, the spindle 21a). The electric motor 30 is provided integrally with the drive shaft 21 in the first region V1 of the housing 10. The electric motor 30 includes a rotor 31 and a stator core unit 32 arranged on the radial outer side of the rotor 31. For example, a direct current from a vehicle battery (not shown) is converted into an alternating current by the inverter 40 and supplied to the electric motor 30. The rotor 31 is rotatably supported inside the stator core unit 32 via a spindle 21a fitted (for example, press-fitted) into a shaft hole formed at the center of the rotor 31 in the radial direction. When a magnetic field is generated in the stator core unit 32 by the power supply from the inverter 40, rotational power acts on the rotor 31 to rotationally drive the spindle 21a. Further, the flange portion 21a1 of the drive shaft 21 is arranged between the electric motor 30 and the thrust receiving portion 24 in the first region V1.

Then, the electric motor 30 is provided by a plurality of holding members 33 provided at intervals in the circumferential direction between the outer peripheral surface of the stator core unit 32 and the inner peripheral surface of the peripheral wall portion 11a of the housing 10 (center housing 11). It is held against the housing 10. There is a gap between the holding members 33. Therefore, the refrigerant can flow around the electric motor 30.

In the scroll type compressor 100 configured as described above, when the spindle 21a is rotationally driven by the electric motor 30, the eccentric shaft 21b is moved along with the swivel bearing 22 and the swing member 23, and the axis X'of the fixed scroll 2 is It revolves around, and this revolving driving force is transmitted to the movable scroll 3 via the connecting pin 25a. At this time, the movable scroll 3 is integrally coupled with the swing member 23 via the connecting pin 25a, and revolves and turns integrally with the swing member 23. The scroll type compressor 100 compresses the refrigerant flowing into the closed space S between the fixed scroll 2 and the movable scroll 3 by this revolving turning motion.

Next, the impeller 27 and the counterweight 28 will be described in detail with reference to FIGS. 1, 2, and 7 to 9. 7 is a front view of the impeller 27, FIG. 8 is a cross-sectional view taken along the line BB shown in FIG. 7, and FIG. 9 is a cross-sectional view taken along the line CC shown in FIG.

In the present embodiment, the impeller 27 has an annular shape connecting the hub 27a to which the drive shaft 21 is fitted, the plurality of blades 27b radially extending from the outer peripheral surface of the hub 27a, and the tips of the plurality of blades 27b. It has a rim portion 27c. The impeller 27 is an impeller for a so-called axial fan that sucks fluid from one end side in the extending direction of the rotation axis (that is, the rotation axis X of the main shaft 21a) and sends the fluid toward the other end. The hub 27a is formed, for example, in a cylindrical shape. Each blade 27b is inclined so that the front end portion in the rotation direction R (see FIGS. 1 and 7) is inclined toward the suction side (lower side in FIGS. 1, 8 and 9), and the blades 27b are viewed from the front (plan view). ) Is formed in the shape of a fan-shaped propeller. The rim portion 27c is provided concentrically with the hub 27a.

In the present embodiment, the impeller 27 is attached to a portion of the drive shaft 21 between the electric motor 30 and the thrust receiving portion 24. Specifically, the impeller 27 is mounted on the outer peripheral surface of the flange portion 21a1 integrally formed with the eccentric shaft 21b of the drive shaft 21. That is, the flange portion 21a1 is fitted inside the hub 27a of the impeller 27, and the impeller 27 is arranged in the region between the electric motor 30 and the thrust receiving portion 24 in the first region V1. Then, in the present embodiment, at least the thrust receiving portion 24, the swivel bearing 22, and the swing member 23 are arranged between the impeller 27 and the movable scroll 3. Further, the rim portion 27c of the impeller 27 has a thickness equivalent to that of the flange portion 21a1 and is arranged so as to be substantially flush with the flange surface of the flange portion 21a1.

In the present embodiment, an inclined surface 27c1 is formed on the inner surface of the rim portion 27c so as to approach the outer peripheral side of the rim portion 27c toward the thrust receiving portion 24 side.

In the present embodiment, the impeller 27 rocks when the gap between the outer peripheral surface of the impeller 27 (specifically, the rim portion 27c) and the inner peripheral surface of the housing 10 (specifically, the center housing 11) swings. It is formed so as to be smaller than the minimum gap between the outer peripheral surface of the moving member 23 and the inner peripheral surface of the housing 10. That is, the impeller 27 has a gap between the impeller 27 and the inner peripheral surface of the housing 10 so that the impeller 27 can rotate, and this gap is set to be, for example, less than 1 mm, preferably less than 0.5 mm. ing. In the present embodiment, the impeller 27 is arranged inside the annular projecting portion 11b projecting inside the center housing 11, and is located between the inner peripheral surface of the projecting portion 11b and the rim portion 27c. The gap is formed so as to be smaller than the minimum gap between the outer peripheral surface of the swing member 23 and the inner peripheral surface of the housing 10.

In the present embodiment, the counterweight 28 is provided integrally with the impeller 27. Specifically, the counterweight 28 is provided so as to project inside the rim portion 27c at an angular position in the circumferential direction opposite to the eccentric direction of the eccentric shaft 21b with respect to the rotation axis X in the rim portion 27c. .. Further, the inclined surface 27c1 of the rim portion 27c is also formed inside the counterweight 28, and is formed in an annular shape as a whole.

Next, the flow of the refrigerant in the scroll type compressor 100 will be described.
When the drive shaft 21 rotates, the movable scroll 3 revolves around the axis X'of the fixed scroll 2, and the impeller 27 rotates. Due to the rotation of the impeller 27, a flow of refrigerant is generated in the first region V1 from the end region V11 side opposite to the thrust receiving portion 24 toward the thrust receiving portion 24 side. Then, the refrigerant from the low pressure side of the refrigerant circuit is introduced into the first region V1 (end region V11) via the suction port P1 and is introduced into the electric motor 30 and around the electric motor 30 (specifically, the motor winding). The electric motor 30 is cooled by passing through gaps between lines, gaps between teeth, gaps between holding members 33, etc., and then flows between the blades 27b of the impeller 27 to the thrust receiving portion 24 side. Is sent to. Therefore, in the present embodiment, the impeller 27 is provided on the downstream side of the electric motor 30 in the flow direction of the refrigerant with respect to the electric motor 30. The refrigerant is generally sent toward the thrust receiving portion 24 side along the extension direction of the rotation axis of the impeller 27, but a part of the refrigerant is radially outward of the impeller 27 along each blade 27b by centrifugal force. It flows and collides with the inclined surface 27c1 of the rim portion 27c. The refrigerant that collides with the inclined surface 27c1 is sent out to the thrust receiving portion 24 side by the inclined surface 27c1. The refrigerant sent out from the impeller 27 is then pushed into the fluid intake region H1 near the outer end of the spiral of the scroll unit 1 through the communication hole 24a1 as the refrigerant introduction passage and the recess of the outer edge of the rocking member 23. Is taken into the fluid uptake region H1. Then, the refrigerant taken into the fluid intake region H1 is compressed in the closed space S via the outer ends of the spirals of the first lap 2b and the second lap 3b. The compressed refrigerant is discharged to the discharge chamber H2 via the discharge hole 2a1 and the one-side valve 18, and then discharged from the discharge chamber H2 to the high pressure side of the refrigerant circuit via a discharge port (not shown). That is, in the present embodiment, the refrigerant flowing into the first region V1 from the suction port P1 cools the electric motor 30 in the housing 10 and takes fluid through the communication holes 24a1 by the blowing action of the impeller 27. It is pushed into the filling region H1 and boosted.

In the scroll type compressor 100 according to the present embodiment, the space in the housing 10 is divided into the first region V1 and the second region V2 by the thrust receiving portion 24, and the communication hole 24a1 in the thrust receiving portion 24 is used to divide the space inside the housing 10. One region V1 and the fluid intake region H1 are communicated with each other. Then, the refrigerant in the first region V1 is sent out to the thrust receiving portion 24 side by the impeller 27 attached to the drive shaft 21 in the first region V1. Therefore, the refrigerant in the first region V1 is pushed into the fluid intake region H1 by the impeller 27 through the communication hole 24a1 and is taken into the fluid intake region H1. That is, the blower including the impeller 27, the drive shaft 21, and the housing 10 has a function as a so-called supercharger. Then, the refrigerant taken into the fluid intake region H1 is compressed and discharged in the closed space S via the outer ends of the spirals of the first lap 2b and the second lap 3b. Therefore, in the scroll type compressor 100, the refrigerant in the first region V1 can be pushed into the fluid intake region H1 to increase the pressure, so that the amount of fluid flowing into the closed space S from the fluid intake region H1 ( The mass flow rate) can be increased as compared with the case where the fluid is flowed in as it is without being boosted, and the amount of the compressed refrigerant to be discharged can be increased. Therefore, when the capacity required for the compressor (for example, the amount of discharged gas) is the same, the volume of the closed space S can be made smaller than before, so that the compressor can be made smaller than before. Further, when the size of the compressor may be the same as the conventional one, the capacity of the compressor can be increased while maintaining the size of the compressor. In this way, it is possible to provide the scroll type compressor 100 that can be effectively miniaturized.

Here, in the conventional scroll type compressor, the pressure of the refrigerant sucked into the scroll type compressor from the low pressure side of the refrigerant circuit in the heating operation (refrigerant suction pressure) is lower than the suction pressure of the refrigerant in the cooling operation. If nothing is done, it may be difficult to obtain a sufficient heating capacity (for example, the amount of discharged gas). In this respect, the scroll type compressor 100 according to the present embodiment can increase the pressure of the sucked refrigerant by the impeller 27 even if the low pressure, that is, the low density refrigerant is sucked in the heating operation. As a result, the amount of the compressed refrigerant to be discharged can be increased. That is, the scroll type compressor 100 is a compressor suitable for a refrigerant circuit capable of heating operation.

In the present embodiment, an inclined surface 27c1 is formed on the inner surface of the rim portion 27c of the impeller 27 so as to approach the outer peripheral side of the rim portion 27c toward the thrust receiving portion 24 side. As a result, in the impeller 27 for so-called axial flow fans, even if a refrigerant flow is generated outward in the radial direction of the impeller 27 due to centrifugal force, the direction of the refrigerant flow is changed by the inclined surface 27c1 and the thrust receiving portion 24 The refrigerant can be guided so that it flows to the side (that is, in the direction of the rotation axis of the impeller).

In the present embodiment, a plurality of through holes 24a are formed in the outer edge portion of the thrust receiving portion 24, and the drive mechanism 20 penetrates the through holes 24a and the outer edge portion of the swing member 23 and the movable scroll 3. It has a connecting pin 25a that connects the second bottom plate 3a to the outer edge portion. Therefore, when the spindle 21a is rotationally driven, the eccentric shaft 21b revolves around the axis X'of the fixed scroll 2 together with the swing bearing 22 and the swing member 23, and this revolution driving force is transmitted via the connecting pin 25a. Is transmitted to the movable scroll 3. In this way, the revolution driving force that causes the movable scroll 3 to revolve around the axis X'of the fixed scroll 2 is stably transmitted by the connecting pin 25a, so that the movable scroll 3 is caused by the transmission structure of the revolution driving force. Distortion of the second bottom plate 3a can be suppressed or prevented, and thus deterioration of the performance of the compressor can be suppressed or prevented.

In the present embodiment, at least the thrust receiving portion 24, the swivel bearing 22 and the swing member 23 are arranged between the impeller 27 and the movable scroll 3, so that the drive mechanism 20 other than the drive shaft 21 is configured. The members can be integrated between the impeller 27 and the movable scroll 3. As a result, the size of the compressor can be reduced more efficiently.

In the present embodiment, the impeller 27 has the outer circumference of the swing member 23 when the gap between the outer peripheral surface of the rim portion 27c and the inner peripheral surface of the housing 10 (protruding portion 11b of the center housing 11) swings. It is formed so as to be smaller than the minimum gap between the surface and the inner peripheral surface of the housing 10 (protruding portion 11b). As a result, the refrigerant sent from the impeller 27 to the thrust receiving portion 24 side passes through the gap between the outer peripheral surface of the rim portion 27c and the inner peripheral surface of the housing 10 (protruding portion 11b of the center housing 11). It is possible to prevent or suppress backflow to one region V1. As a result, the refrigerant can be effectively pushed into the fluid uptake region H1.

In the present embodiment, the rotation prevention mechanism portion 25 is composed of a through hole 24a and a connecting pin 25a, and the intermediate portion of the connecting pin 25a is in sliding contact with the hole wall surface of the through hole 24a to prevent the movable scroll 3 from rotating. Therefore, the hole wall surface of the through hole 24a is slid over the entire wall surface of the through hole 24a in the hole depth direction (that is, the entire thickness of the thrust receiving portion 24 in the present embodiment). It can be effectively used as a contact surface. Further, the connecting pin 25a of the drive mechanism 20 has a function of preventing the rotation of the movable scroll 3 in addition to the function of transmitting the revolution driving force. Thereby, the structure of the drive mechanism 20 can be simplified.

In the present embodiment, the communication hole 24a1 that communicates the first region V1 and the fluid intake region H1 in the second region V2 is composed of at least a part of the plurality of through holes 24a. That is, a part of the through hole 24a has not only a function as a rotation prevention mechanism portion 25 but also a function as a refrigerant introduction passage for introducing the refrigerant from the first region V1 to the fluid intake region H1. .. Therefore, it is not necessary to separately form the refrigerant introduction passage in the housing 10 or the like, and the productivity of the scroll type compressor 100 or the like can be improved. Further, the recess on the outer edge of the rocking member 23 also has a function as a refrigerant introduction passage, and has the same effect as the through hole 24a.

In the present embodiment, the electric motor 30 is provided integrally with the drive shaft 21 (spindle 21a) in the first region V1, and the opening end P11 on the first region V1 side of the suction port P1 is the thrust receiving portion 24 in the first region V1. It is opened in the end region V11 on the opposite side to the above. As a result, when the impeller 27 provided in the first region V1 is rotated, the refrigerant flows into the first region V1 from the end region V11 side opposite to the thrust receiving portion 24 toward the thrust receiving portion 24 side. A flow can be generated. Therefore, a flow of the refrigerant passing through the electric motor 30 and its surroundings can be formed in the housing 10, and the electric motor 30 can be efficiently cooled by the refrigerant. Further, in the present embodiment, the impeller 27 is attached to a portion of the drive shaft 21 between the electric motor 30 and the thrust receiving portion 24. As a result, it is possible to construct a structure in which the impeller 27 is arranged on the downstream side of the electric motor 30 in the flow direction of the refrigerant.

In this embodiment, the counterweight 28 is integrally formed with the impeller 27. As a result, the manufacturing cost of the counterweight 28 can be reduced. The counterweight 28 is formed on the rim portion 27c, which is the outermost diameter portion of the impeller 27. Therefore, the position of the center of gravity of the counterweight 28 can be moved away from the rotation axis X of the main shaft 21a only by increasing the outer diameter of the rim portion 27c as much as possible. As a result, the counterweight 28 can be effectively reduced in weight.

In the present embodiment, the back pressure chamber H3 is partitioned as one space by the back surface of the second bottom plate 3a, the movable scroll side end surface of the thrust receiving portion 24, and one annular seal member 19. However, it is not limited to this. The back pressure chamber H3 may be divided into a plurality of regions as shown in FIG. 10, which is a schematic cross-sectional view for explaining a modification of the scroll type compressor 100. In this case, the back pressure chamber H3 is multiplexed between the back surface of the second bottom plate 3a, the movable scroll side end surface of the thrust receiving portion 24, and the back surface of the second bottom plate 3a and the movable scroll side end surface of the thrust receiving portion 24. A plurality of (two in FIG. 10) sealing

members

19 and 19 arranged in an annular shape divide the area into a plurality of (two in FIG. 10) regions. Then, the communication passage 3d that penetrates the second bottom plate 3a of the movable scroll 3 and communicates the closed space S and the back pressure chamber H3 is opened corresponding to each region of the plurality of regions of the back pressure chamber H3. To. Each region of the plurality of regions of the back pressure chamber H3 communicates with the closed space S in which the continuous passage 3d opens among the plurality of closed spaces S via the communication passage 3d corresponding to the region. As a result, the pressure distribution of the entire back pressure acting on the back surface of the second bottom plate 3a can be roughly matched with the overall pressure distribution of the plurality of closed spaces S acting on the end faces of the second bottom plate 3a on the closed space S side. .. Further, since the communication passage 3d simply penetrates the second bottom plate 3a in the plate thickness direction, the flow path length is short and the flow path is simple. Therefore, the pressure loss in the flow process of the refrigerant through the communication passage 3d can be suppressed to a low level. As a result, in the scroll type compressor 100 shown in FIG. 10, the load imbalance between the load in the thrust direction and the back pressure load acting on the movable scroll 3 can be effectively reduced.

Further, in the present embodiment, the impeller 27 has an annular rim portion 27c connecting the tip portions of the plurality of blades 27b, but the impeller portion 27c may not be provided. Further, although the blades 27b are formed in a substantially fan-shaped propeller shape, the shape of the blades 27b is not limited to this. Further, an inclined surface 27c1 is formed on the inner surface of the rim portion 27c, and the inclined surface 27c1 guides the flow of the refrigerant. However, the present invention is not limited to this, and the member for guiding the flow of the refrigerant is separated from the impeller 27. It may be provided. Further, although the swivel bearing 22 and the rear bearing 26 are made of a sliding bearing, the present invention is not limited to this, and a rolling bearing may be used. Further, the eccentric shaft 21b is composed of one component, but is not limited to this, and may be composed of two components, an eccentric bush and a collar. The counterweight 28 is integrally formed with the impeller 27, but the present invention is not limited to this, and the counterweight 28 may be integrally formed with the drive shaft 21, or the impeller 27 may be formed as a separate component from the impeller 27 and the drive shaft 21. Or may be attached to the drive shaft 21. The rotation prevention mechanism portion 25 is composed of a through hole 24a and a connecting pin 25a, but is not limited to this. For example, the rotation prevention mechanism portion 25 may employ an Oldham coupling method, or a ball coupling method in which a ball coupling is provided between the back surface of the second bottom plate 3a of the movable scroll 3 and the thrust receiving portion 24. May be adopted.

FIG. 11 is a schematic cross-sectional view for explaining another modified example of the scroll type compressor 100, and FIG. 12 is a front view of the impeller 27 in the modified example shown in FIG. In the present embodiment, the impeller 27 is attached to a portion of the drive shaft 21 between the electric motor 30 and the thrust receiving portion 24, but the present invention is not limited to this, and as shown in FIG. It may be attached to a portion of the drive shaft 21 between the end portion 211 on the opposite side of the thrust receiving portion 24 and the electric motor 30. In this case, the impeller 27 is provided on the upstream side of the electric motor 30 in the flow direction of the refrigerant with respect to the electric motor 30.

Specifically, as shown in FIG. 11, the impeller 27 has an end surface of the electric motor 30 opposite to the thrust receiving portion 24 and a surface of the front housing 12 on the box bottom 12a opposite to the inverter 40 (first). It is located between the area V1 side surface). In other words, the impeller 27 is located upstream of the electric motor 30 in the flow direction of the refrigerant, and is arranged in the end region V11 on the inverter 40 side in the first region V1.

Also, the impeller 27 is not limited to those for axial fans. For example, as shown in FIGS. 11 and 12, the impeller 27 may be for a centrifugal fan. Specifically, the impeller 27 for a centrifugal fan has a disk-shaped base 271 attached to a drive shaft 21 and a plurality of centrifugal blades 272 formed on an end surface of the base 271 opposite to the electric motor 30. Have. A cylindrical boss portion 273 is provided at the center portion in the radial direction of the base 271. The drive shaft 21 is fitted into the boss portion 273. The impeller 27 is attached to the drive shaft 21 so that the end surface of the base 271 on the centrifugal blade 272 side faces the box bottom portion 12a.

Further, as shown in FIG. 11, the suction port P1 may be formed, for example, on the box bottom 12a of the front housing 12 facing the base 271 of the impeller 27. Also in this case, the opening end P11 on the first region V1 side of the suction port P1 is opened in the end region V11 on the opposite side of the thrust receiving portion 24 in the first region V1. Specifically, the opening end P11 on the first region V1 side of the suction port P1 faces the end surface on the centrifugal blade 272 side of the base 271 of the impeller 27. The opening end P11 on the first region V1 side of the suction port P1 may be located inward in the radial direction with respect to the outer peripheral surface of the impeller 27. Specifically, the suction port P1 has a radial flow path portion extending from the outer peripheral surface of the box bottom portion 12a toward the center side (support portion 12a1 side) and the inside of the support portion 12a1 parallel to the rotation axis X of the drive shaft 21. It has an extending axial flow path portion. In the present embodiment, the opening end P11 on the first region V1 side of the suction port P1 is open in the vicinity of the drive shaft 21 in the radial direction. As a result, the refrigerant from the suction port P1 is efficiently taken into the impeller 27.

Further, as shown in FIG. 11, when the impeller 27 is arranged on the upstream side of the electric motor 30 in the flow direction of the refrigerant, the scroll type compressor 100 is located on the outer peripheral surface of the electric motor 30 and the housing 10. It is preferable to further include a sealing member 34 that seals the gap between the inner peripheral surface (the inner peripheral surface of the peripheral wall portion 11a of the center housing 11). The seal member 34 is formed so as to fill a gap between the outer peripheral surface of the electric motor 30 and the inner peripheral surface of the peripheral wall portion 11a. For example, the seal member 34 is formed in a tubular shape and has the outer peripheral surface and the peripheral wall of the electric motor 30. It exists over the entire circumference in the circumferential direction with the inner peripheral surface of the portion 11a.

Next, the flow of the refrigerant (indicated by the white arrow in FIG. 11) in the modified example shown in FIG. 11 will be described. When the impeller 27 rotates, the refrigerant from the low pressure side of the refrigerant circuit is guided to the end region V11 on the opposite side of the thrust receiving portion 24 in the first region V1 via the suction port P1. The refrigerant guided from the opening end P11 on the first region V1 side of the suction port P1 into the end region V11 is directed radially outward from the radial center side of the base 271 by the centrifugal force generated by the rotation of the impeller 27. Flows. At this time, the box bottom 12a is cooled by the refrigerant flowing in the suction port P1 and the refrigerant flowing in the end region V11, and as a result, the inverter 40 is cooled. Specifically, in the end region V11 of the first region V1, a flow of the refrigerant is generated along the box bottom portion 12a and from the radial center side to the radial outer side. That is, when the impeller 27 rotates, the flow of the refrigerant (fluid) along the box bottom portion 12a is generated in the end region V11 of the first region V1. The flow of the refrigerant cools the inverter 40 more effectively. Here, when the impeller 27 rotates, velocity energy is applied to the refrigerant. The width of the flow path of the refrigerant composed of the adjacent

centrifugal blades

272 and 272 becomes wider toward the outer side in the radial direction. Therefore, the refrigerant decelerates toward the outer side in the radial direction in the flow path, and the velocity energy is converted into pressure energy, and as a result, the pressure of the refrigerant guided into the end region V11 is increased by the impeller 27. .. In the modified example shown in FIG. 11, since the impeller 27 is arranged on the upstream side of the electric motor 30 in the flow direction of the refrigerant, the refrigerant compressed by the impeller 27 is the impeller 27 and the peripheral wall portion 11a. It is positively sent to the electric motor 30 side through the gap between the two. As a result, the refrigerant positively sent to the electric motor 30 side passes through the electric motor 30 and effectively cools the electric motor 30 (specifically, the motor winding or the like). Then, the refrigerant flows out from the end surface of the electric motor 30 on the thrust receiving portion 24 side and flows to the thrust receiving portion 24 side. The refrigerant flowing to the thrust receiving portion 24 side then enters the fluid intake region H1 near the outer end of the spiral of the scroll unit 1 via the communication hole 24a1 as the refrigerant introduction passage and the recess of the outer edge portion of the swing member 23. It is pushed in and taken into the fluid uptake region H1. That is, even in the modified example shown in FIG. 11, the refrigerant flowing into the first region V1 from the suction port P1 is pushed into the fluid intake region H1 via the communication hole 24a1 by the blowing action of the impeller 27 and boosted. Has been done. Therefore, even in the modified example shown in FIG. 11, the blower including the impeller 27, the drive shaft 21, and the housing 10 has a function as a so-called supercharger.

Here, in the modified example shown in FIG. 11, since the seal member 34 is provided between the outer peripheral surface of the electric motor 30 and the inner peripheral surface of the peripheral wall portion 11a of the center housing 11, the thrust receiver in the electric motor 30 is received. It is possible to prevent or suppress the refrigerant flowing out from the end surface on the portion 24 side from flowing back to the end region V11 through the gap between the electric motor 30 and the peripheral wall portion 11a. As a result, the refrigerant can be effectively pushed into the fluid uptake region H1. Further, by providing the seal member 34, the refrigerant flows more effectively in the electric motor 30, so that the electric motor 30 can be cooled more effectively. Further, in the modified example shown in FIG. 11, since the impeller 27 is provided upstream of the electric motor 30 in the flow direction of the refrigerant, the refrigerant before being heated by the electric motor 30 is the impeller 27. Is taken in by. Therefore, the impeller 27 takes in and compresses the refrigerant before the specific volume becomes large (the density becomes low) due to heating. As a result, the scroll type compressor 100 shown in FIG. 11 has a fluid intake region H1 more than the scroll type compressor 100 shown in FIG. 1 in which the impeller 27 is provided downstream of the electric motor 30 in the flow direction. The amount of fluid (mass flow rate) flowing into the closed space S can be increased, and the amount of compressed refrigerant to be discharged can be increased more effectively. In the modified example shown in FIG. 11, the seal member 34 is provided between the outer peripheral surface of the electric motor 30 and the inner peripheral surface of the peripheral wall portion 11a of the center housing 11, but the seal member 34 is not provided. May be good.

In the above description, the scroll type compressor 100 has one impeller 27, but the present invention is not limited to this, and a plurality of impellers 27 may be provided. That is, the impeller 27 may be provided in multiple stages. Specifically, the impeller 27 is provided not only on either the upstream side or the downstream side in the flow direction of the electric motor 30, but also on both the upstream side and the downstream side in the flow direction of the electric motor 30. You may.

Further, the scroll type compressor 100 has been described by taking the case of the so-called inverter integrated type as an example, but the present invention is not limited to this, and the scroll type compressor 100 may be separate from the inverter 40. Further, although the electric motor 30 is built in, the electric motor 30 may be provided outside the housing 10. The electric motor 30 is used as the drive source, but the present invention is not limited to this, and the rotational power may be transmitted from the engine of the vehicle to the spindle 21a. Further, the fluid is assumed to be a refrigerant, but the present invention is not limited to this, and an appropriate fluid can be applied.

Although the preferred embodiment of the present invention has been described above, the present invention is not limited to the above-described embodiment and the above-mentioned modification, and various modifications and modifications can be made based on the technical idea of the present invention.

2 ... Fixed scroll, 2b ... 1st lap (lap), 3 ... Movable scroll, 3b ... 2nd lap (lap), 10 ... Housing, 11a ... Circumferential wall, 12a ... Box bottom (bottom wall), 20 ... Drive Mechanism, 21 ... Drive shaft, 21a ... Main shaft, 21b ... Eccentric shaft, 22 ... Swivel bearing, 23 ... Swing member, 24 ... Thrust receiving part, 24a ... Through hole, 24a1 ... Communication hole, 25 ... Rotation prevention mechanism part, 25a ... Connecting pin, 27 ... Impeller, 27a ... Hub, 27b ... Blade, 27c ... Rim part, 27c1 ... Inclined surface, 271 ... Base, 272 ... Centrifugal blade, 28 ... Counter weight, 30 ... Electric motor, 34 ... Seal Member, 40 ... Inverter, 100 ... Scroll compressor, H1 ... Fluid intake area, P1 ... Suction port, P11 ... Open end, S ... Sealed space, V1 ... 1st area, V11 ... End area, V2 ... 2 areas, X ... rotation axis, X'... fixed scroll axis

Claims

A fixed scroll and a movable scroll that have spiral wraps and are meshed with each other, a thrust receiving portion provided on the back side of the movable scroll and receiving the thrust force of the movable scroll, and a revolution driving force transmitted to the movable scroll. A drive shaft forming a part of the drive mechanism for the above is provided in the housing, and the movable scroll revolves to form a closed space between the movable scroll and the fixed scroll whose volume changes with the revolve. A scroll-type compressor that compresses and discharges compressible fluid in a closed space.
The thrust receiving portion is divided into a first region in which the drive shaft extends and the fluid is guided from the outside in the housing and a second region in which the fixed scroll and the movable scroll are arranged, and the thrust receiving portion is described. It has a communication hole that communicates the first region and the fluid intake region near the outer end of the spiral of the lap in the second region.
A scroll type compressor to which an impeller that rotates integrally with the drive shaft and sends the fluid in the first region to the thrust receiving portion side is attached to the drive shaft.
The drive shaft includes a spindle that is rotationally driven around a rotation axis aligned with the axis of the fixed scroll, and an eccentric shaft that is eccentrically provided at one end of the spindle in the axial direction with respect to the rotation axis. Have and
The drive mechanism
With the drive shaft
A swivel bearing mounted on the outer peripheral surface of the eccentric shaft,
An annular swing member mounted on the outer peripheral surface of the swivel bearing, which is arranged so as to sandwich the thrust receiving portion between the movable scroll and the swing member.
With the thrust receiving part
The rotation prevention mechanism unit that prevents the rotation of the movable scroll, and
Including
A plurality of through holes are formed in the outer edge portion of the thrust receiving portion.
The drive mechanism has a connecting pin that penetrates the through hole and connects the outer edge portion of the rocking member and the outer edge portion of the movable scroll, and the revolution driving force is applied via the connecting pin. Transmit to the movable scroll,
The scroll type compressor according to claim 1, wherein at least the thrust receiving portion, the swivel bearing, and the swinging member are arranged between the impeller and the movable scroll.
In the impeller, the minimum gap between the outer peripheral surface of the rocking member and the inner peripheral surface of the housing when the gap between the outer peripheral surface of the impeller and the inner peripheral surface of the housing swings. The scroll type compressor according to claim 2, which is formed so as to be smaller than.
Each of the plurality of through holes is opened in a circular shape.
The connecting pin is formed to have a smaller diameter than the through hole.
The rotation prevention mechanism portion is composed of the through hole and the connecting pin, and the intermediate portion of the connecting pin is slidably contacted with the hole wall surface of the through hole to prevent the movable scroll from rotating.
The scroll type compressor according to claim 2 or 3, wherein the communication hole comprises at least a part of the plurality of through holes.
The scroll type compressor according to any one of claims 1 to 4, wherein a counterweight for ensuring a weight balance with respect to the movable scroll is provided integrally with the impeller.
An electric motor that generates a rotational driving force of the drive shaft is provided integrally with the drive shaft in the first region.
The housing is formed with a suction port for guiding the fluid into the housing from the outside.
The scroll type according to any one of claims 1 to 5, wherein the open end of the suction port on the first region side is opened in the end region on the opposite side of the thrust receiving portion in the first region. Compressor.
The scroll type compressor according to claim 6, wherein the impeller is attached to a portion of the drive shaft between the electric motor and the thrust receiving portion.
The scroll type compressor according to claim 6, wherein the impeller is attached to a portion of the drive shaft between the end of the drive shaft on the opposite side of the thrust receiving portion and the electric motor.
The scroll type compressor according to claim 8, further comprising a sealing member for sealing a gap between the outer peripheral surface of the electric motor and the inner peripheral surface of the housing.
The impeller has a hub to which the drive shaft is fitted, a plurality of blades extending radially from the outer peripheral surface of the hub, and an annular rim portion connecting between the tips of the plurality of blades.
The method according to any one of claims 1 to 9, wherein an inclined surface is formed on the inner surface of the rim portion so as to be closer to the outer peripheral side of the rim portion toward the thrust receiving portion side. Scroll type compressor.
The scroll according to claim 8 or 9, wherein the impeller has a disk-shaped base attached to the drive shaft and a plurality of centrifugal blades formed on an end surface of the base opposite to the electric motor. Mold compressor.
An inverter that controls the drive of the electric motor
Including more
The housing has a tubular peripheral wall portion having the first region and the second region inside, and a bottom wall portion that closes the opening on the first region side in the peripheral wall portion.
The inverter is fixed to the surface of the bottom wall portion opposite to the first region.
The scroll type compressor according to claim 11, wherein when the impeller rotates, a flow of the fluid along the bottom wall portion is generated in the end region of the first region.