JP7166177B2 - scroll type fluid machinery - Google Patents

Description

The present invention relates to a scroll-type fluid machine that has a fixed scroll and a movable scroll that mesh with each other, and compresses or expands a fluid by changing the volume of a closed space formed by these scrolls.

A scroll-type fluid machine includes a fixed scroll and a movable scroll that are meshed with each other, and a drive mechanism for preventing rotation of the movable scroll and for transmitting a revolving driving force about the axis of the fixed scroll to the movable scroll. The orbiting scroll revolves while being in contact with the fixed scroll, and forms a sealed space between the fixed scroll and the fixed scroll whose volume changes as it revolves.

As this type of scroll-type fluid machine, for example, a scroll-type compressor described in Patent Document 1 (hereinafter referred to as a scroll-type fluid machine) is generally known. The drive mechanism in the scroll-type fluid machine described in Patent Document 1 includes an orbiting scroll member (hereinafter referred to as a movable scroll) as the movable scroll and a fixed scroll member (hereinafter referred to as a fixed scroll) as the fixed scroll. ), and a rotation prevention mechanism for preventing rotation of the movable scroll.

Specifically, in the scroll-type fluid machine disclosed in Patent Document 1, the driving force transmission mechanism includes a rotating shaft that is rotationally driven (hereinafter, referred to as a driving shaft) and an axis of the driving shaft at one end in the axial direction of the driving shaft. An eccentric shaft provided eccentrically with respect to the center, an eccentric bush fitted on the outer peripheral surface of the eccentric shaft, and a mounting portion (hereinafter referred to as a cylindrical boss portion) protruding cylindrically from the back side of the bottom plate of the movable scroll ), and a slewing bearing comprising a slide bearing mounted between the outer peripheral surface of the eccentric bushing and the inner peripheral surface of the cylindrical boss portion. As a result, when the drive shaft is rotationally driven by the power of an external engine or the like, the rotational power of the drive shaft is converted into the revolution driving force, and this revolution driving force is transmitted to the cylindrical boss portion of the movable scroll. A movable scroll revolves around the axis of the fixed scroll. Further, in the scroll-type fluid machine of Patent Document 1, a thrust plate that receives the thrust force of the movable scroll is provided between the inner end surface of the front block that constitutes the housing and the rear surface of the movable scroll, and is fixed to the front block. there is A so-called pin-and-hole mechanism consisting of a pin and a hole is employed as the rotation-preventing mechanism. The slide holes are formed in the thrust plate so as to correspond to the respective pins. As a result, the outer peripheral surface of the tip of the pin slides along the hole wall surface of the sliding hole, and as a result, rotation of the orbiting scroll is prevented.

JP-A-11-44295

However, in the driving force transmission mechanism in the scroll-type fluid machine described in Patent Document 1, the eccentric bushing and the orbiting bearing are provided inside a cylindrical boss portion which is cylindrically projected from the back side of the bottom plate of the movable scroll. It is In the case of such a structure, the orbiting bearing is generally press-fitted into the cylindrical boss and fixed. Therefore, the bottom plate of the orbiting scroll may be distorted according to the deformation of the cylindrical boss portion due to this press-fitting. As a result, there is a problem that an excessively large gap is generated between the bottom plate of the orbiting scroll and the tip of the spiral wrap of the fixed scroll, and the performance of the scroll-type fluid machine tends to be deteriorated.

SUMMARY OF THE INVENTION It is an object of the present invention to provide a scroll-type fluid machine capable of suppressing or preventing deterioration in performance caused by distortion of the bottom plate of a movable scroll.

According to one aspect of the present invention, a fixed scroll and a movable scroll, each having a bottom plate and a spiral wrap erected on the bottom plate and engaged with each other; a drive mechanism for transmitting a driving force for revolution about the axis of the fixed scroll is provided in the housing, and the orbiting scroll revolves while being in contact with the fixed scroll and moves between the fixed scroll and the fixed scroll along with the revolution. A scroll-type fluid machine that forms an enclosed space whose volume changes is provided. The drive mechanism includes a crankshaft, a turning bearing, an annular swinging member, a thrust receiving portion, and a rotation preventing mechanism. The crankshaft includes a drive shaft that is rotatably driven around a rotation axis aligned with the axis of the fixed scroll, and an eccentric that is provided eccentrically with respect to the rotation axis at one end in the axial direction of the drive shaft. has an axis. The slewing bearing is fitted with the eccentric shaft. The annular rocking member is fitted onto the outer peripheral surface of the orbiting bearing. The thrust receiving portion is provided between the bottom plate of the orbiting scroll and the oscillating member, and receives a thrust force of the orbiting scroll. The rotation prevention mechanism prevents rotation of the orbiting scroll. The drive mechanism has a connecting pin that passes through a plurality of through holes penetrating the outer edge of the thrust receiving portion and connects between the outer edge of the swing member and the outer edge of the bottom plate of the orbiting scroll. and transmits the revolution driving force to the orbiting scroll via the connecting pin.

In the scroll-type fluid machine according to the aspect, the drive mechanism includes a drive shaft that is rotationally driven around a rotation axis aligned with the axis of the fixed scroll, and a drive shaft that rotates at one end in the axial direction of the drive shaft. A crankshaft having an eccentric shaft provided eccentrically with respect to the axis, a swivel bearing fitted with the eccentric shaft, an annular swinging member fitted on the outer peripheral surface of the swivel bearing, and the orbiting scroll. A thrust receiving portion provided between the bottom plate and the swinging member for receiving the thrust force of the orbiting scroll; and a rotation prevention mechanism portion for preventing rotation of the orbiting scroll. It has a connecting pin that penetrates through a plurality of through holes penetrating the outer edge of the thrust receiving portion and connects between the outer edge of the swing member and the outer edge of the bottom plate of the orbiting scroll. Therefore, when the drive shaft is rotationally driven, the eccentric shaft revolves around the axis of the fixed scroll together with the orbiting bearing and the swinging member, and this revolving driving force is transmitted through the connecting pin. It is transmitted to the movable scroll. That is, the orbiting scroll is integrally connected to the swinging member via the connecting pin, and revolves integrally with the swinging member. In this way, the orbital driving force that causes the orbiting scroll to revolve around the axis of the fixed scroll is transmitted by the connecting pin. Distortion is suppressed or prevented, and in turn, suppression or prevention of deterioration in performance of the scroll fluid machine can be achieved.

In this way, it is possible to provide a scroll-type fluid machine capable of suppressing or preventing deterioration in performance caused by distortion of the bottom plate of the orbiting scroll.

1 is a schematic cross-sectional view of a scroll-type fluid machine according to a first embodiment of the present invention; FIG. FIG. 2 is a cross-sectional view taken along line AA of FIG. 1; 2 is a front view of a crankshaft of the scroll type fluid machine; FIG. FIG. 4 is a front view of a swing member of the scroll type fluid machine; 4 is a front view of a thrust receiving portion of the scroll type fluid machine; FIG. FIG. 4 is a rear view of a movable scroll of the scroll-type fluid machine; It is a schematic sectional view of the scroll type fluid machine in 2nd Embodiment of this invention. FIG. 8 is a cross-sectional view of the main part taken along line BB in FIG. 7; FIG. 8 is a partial front view of the crankshaft of the scroll-type fluid machine shown in FIG. 7; FIG. 8 is a front view of part of the eccentric shaft of the scroll-type fluid machine shown in FIG. 7; FIG. 8 is a front view of a swing member of the scroll-type fluid machine shown in FIG. 7; It is a schematic sectional view for demonstrating the modification of the rotation prevention mechanism part of the said scroll type fluid machine. 13 is a front view of the swing member shown in FIG. 12; FIG. 13 is a front view of the thrust receiving portion 24 shown in FIG. 12; FIG. 13 is a front view of an Oldham ring of the rotation prevention mechanism shown in FIG. 12; FIG.

BEST MODE FOR CARRYING OUT THE INVENTION Hereinafter, embodiments of the present invention will be described in detail. The scroll-type fluid machine according to the present invention can be used as a compressor or an expander, but the example of the compressor will be explained here.

First, a first embodiment of the present invention will be described with reference to FIGS. 1 to 6. FIG.
FIG. 1 is a schematic cross-sectional view showing the overall configuration of a scroll-type fluid machine according to this embodiment, and FIG. 2 is a cross-sectional view taken along line AA in FIG. 3 to 6 are parts diagrams of the scroll type fluid machine, respectively. FIG. 3 is a front view of the crankshaft, FIG. 4 is a front view of the rocking member, FIG. 5 is a front view of the thrust receiving portion, and FIG. It is a rear view of a scroll.

A scroll-type fluid machine 100 according to the present embodiment is a compressor that is incorporated in, for example, a refrigerant circuit of a vehicle air conditioner, and that compresses and discharges refrigerant (fluid) sucked from the low-pressure side of the refrigerant circuit. This scroll-type fluid machine 100 includes a scroll unit 1 , a housing 10 , and a drive mechanism 20 that transmits driving force to the scroll unit 1 . The scroll unit 1 and the drive mechanism 20 are provided inside the housing 10 . In this embodiment, the scroll-type fluid machine 100 also includes an electric motor 30 as a drive source for the scroll unit 1 inside the housing 10 . Further, the scroll type fluid machine 100 includes an inverter 40 for driving and controlling the electric motor 30 inside the housing 10, and an example of a so-called inverter-integrated electric compressor will be described.

The scroll unit 1 has a fixed scroll 2 and a movable scroll 3 that are meshed with each other, as shown in FIG. In the scroll type fluid machine 100, the orbiting scroll 3 revolves around the axis X′ of the fixed scroll 2 while being in contact with the fixed scroll 2, and between the movable scroll 2 and the fixed scroll 2, a sealed space S, which changes in volume as it revolves, is formed. configured to form Further, in this embodiment, the scroll unit 1 is configured to compress the refrigerant in the sealed space S and discharge it. For example, the fixed scroll 2 and movable scroll 3 are made of aluminum alloy.

Specifically, the fixed scroll 2 includes a first bottom plate 2a formed in a disk shape and having a discharge hole 2a1 at the center thereof, and a spiral first bottom plate 2a erected on one end face of the first bottom plate 2a. and a wrap 2b. The movable scroll 3 includes 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 the one end surface of the second bottom plate 3a. have Also, 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. As shown in FIG. In this embodiment, the first bottom plate 2a and the first wrap 2b correspond to the "bottom plate" and "wrap" of the "fixed scroll" according to the present invention, and the second bottom plate 3a and the second wrap 3b correspond to the present invention. It corresponds to the "bottom plate" and "wrap" of the "movable scroll".

The fixed scroll 2 and the movable scroll 3 are arranged so that the first wrap 2b and the second wrap 3b are meshed with each other. Specifically, the fixed scroll 2 and the orbiting scroll 3 are arranged such that the side wall of the first wrap 2b and the second wrap 3b are separated from each other by the circumferential angle of the first wrap 2b and the circumferential angle of the second wrap 3b. The sidewalls of 3b are arranged to partially contact each other. As a result, a crescent-shaped sealed space S (a compression chamber in this embodiment) is formed between the first wrap 2b and the second wrap 3b. That is, a closed space S is formed between the fixed scroll 2 and the movable scroll 3 . In addition, the fixed scroll 2 and the movable scroll 3 have a gap (hereinafter referred to as a first wrap end gap) between the protruding end of the first wrap 2b and the second bottom plate 3a. and the first bottom plate 2a so as to have a gap (hereinafter referred to as a second wrap end gap). In this embodiment, the tip seal member 4 is fitted in the groove formed in the projecting end of the first wrap 2b and the groove formed in the projecting end of the second wrap 3b. The tip seal member 4 appropriately maintains the airtightness of the sealed space S, and as a result, the refrigerant compression performance in the scroll fluid machine 100 is maintained.

More specifically, the fixed scroll 2 has a cylindrical portion 2c erected on the outer edge of the one end face of the first bottom plate 2a. The cylindrical portion 2c has an outer diameter matching the inner diameter of an opening of the housing 10 on one end side (upper side in FIG. 1) of a center housing 11, which will be described later. 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 so as to close one end opening of the center housing 11 .

The orbiting scroll 3 is configured to revolve around the axis X′ of the fixed scroll 2 while being prevented from rotating by the drive mechanism 20 . As a result, the scroll unit 1 moves the closed space S between the fixed scroll 2 and the movable scroll 3 to the central portion and gradually reduces its volume. As a result, the scroll unit 1 compresses within the sealed space S the refrigerant that flows into the sealed space S from the spiral outer end portions of the first wrap 2b and the second wrap 3b.

In the case of an expander, the volume of the sealed space S is increased by moving the sealed space S from the central portion of the first wrap 2b and the second wrap 3b toward the outer end. Then, the fluid taken into the sealed space S from the central portion side of the first wrap 2b and the second wrap 3b is expanded.

The housing 10 has a center housing 11 , a front housing 12 , an inverter cover 13 and a rear housing 14 . These (11, 12, 13, 14) are integrally fastened by fastening members such as bolts 15 to form the housing 10 of the scroll fluid machine 100. As shown in FIG. The housing 10 is made of aluminum alloy, for example.

The center housing 11 has a substantially cylindrical peripheral wall portion 11a and an annular protruding portion 11b that protrudes inward along the inner peripheral surface of the peripheral wall portion 11a in the middle in the longitudinal direction. Inside the center housing 11, the scroll unit 1, the drive mechanism 20, and the electric motor 30 are mainly accommodated. An end surface of the outer edge portion 14a of the rear housing 14 is in contact with one end portion of the peripheral wall portion 11a. A front housing 12 closes the opening on the other end side (lower side in FIG. 1) of the peripheral wall portion 11a.

A suction port P1 into which a refrigerant flows is formed in the peripheral wall portion 11a. Refrigerant from the low-pressure side of the refrigerant circuit is sucked into the center housing 11 through this suction port P1. Therefore, the space inside the center housing 11 functions as a suction chamber H1. The electric motor 30 is cooled by the refrigerant flowing around the electric motor 30 in the suction chamber H1. In FIG. 1, the space above the electric motor 30 communicates with the space below the electric motor 30, and together with the space below the electric motor 30, constitutes one suction chamber H1. In addition, an appropriate amount of lubricating oil is stored in the suction chamber H1 to lubricate the sliding portions of the drive mechanism 20 and the like. Therefore, in the suction chamber H1, the refrigerant flows as a mixed fluid with lubricating oil.

An end surface 11b1 of the protruding portion 11b on the rear housing 14 side is formed as an annular surface orthogonal to a rotation axis X of a drive shaft 21a of the drive mechanism 20, which will be described later. The end surface of the outer edge portion of the thrust receiving portion 24 of the drive mechanism 20, which will be described later, abuts against the end surface 11b1. By sandwiching the fixed scroll 2 between the thrust receiving portion 24 and the rear housing 14 , the fixed scroll 2 is fixed inside the center housing 11 together with the thrust receiving portion 24 .

The front housing 12 is generally formed in the shape of a box with one end open. The box bottom 12a closes the opening on the other end side of the peripheral wall 11a of the center housing 11, and the box bottom 12a protrudes from the outer edge of the box bottom 12a. It has a side wall portion 12b and accommodates an inverter 40 therein. A cylindrical support portion 12a1 that holds a front bearing 16 that supports the end (the lower end in FIG. 1) of the drive shaft 21a protrudes toward the inside of the center housing 11 at the center of the box bottom portion 12a. there is

The inverter cover 13 is formed in a plate shape, closes the one end opening of the front housing 12 , and is fastened to the side wall portion 12 b of the front housing 12 with bolts 15 .

The rear housing 14 is formed in a substantially disc shape having an outer diameter matching the outer diameter of the peripheral wall portion 11a of the center housing 11, and is formed so that its central portion 14b bulges outward. The outer edge portion 14a of the rear housing 14 is fastened to one end portion of the peripheral wall portion 11a by an appropriate number of fastening members such as bolts 15. As shown in FIG.

A radially inner portion 14 a 1 of the outer edge portion 14 a of the rear housing 14 protrudes inward from the inner peripheral surface of the peripheral wall portion 11 a of the center housing 11 . The end face of the inner portion 14a1 abuts against the outer edge of the other end face of the first bottom plate 2a of the fixed scroll 2 (the end face opposite to the end face on the side of the wrap 2b). It is held between the rear housing 14 and the outer edge portion 14a (specifically, the inner portion 14a1). A refrigerant discharge chamber H2 is defined by the bulged central portion 14b of the rear housing 14 and the first bottom plate 2a. A seal member 17 is provided at a contact portion (outer edge portion) of the fixed scroll 2 with the inner portion 14 a 1 of the rear housing 14 . The discharge chamber H2 communicates with the sealed space S via a discharge hole 2a1 formed in the central portion of the first bottom plate 2a. A one-way valve 18 is provided in the discharge chamber H2 so as to cover the opening of the discharge hole 2a1. The one-way valve 18 is a check valve that regulates the flow from the discharge chamber H2 to the closed space S. The refrigerant compressed in the closed space S is discharged through the discharge hole 2a1 and the one-way valve 18 into the discharge chamber H2. 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 14 .

The drive mechanism 20 is a mechanism for preventing the orbiting scroll 3 from rotating and for transmitting to the orbiting scroll 3 a revolving driving force around the axis X′ of the fixed scroll 2 .

As shown in FIGS. 1 and 2, in this embodiment, the drive mechanism 20 includes a crankshaft 21, a turning bearing 22, an annular swinging member 23, a thrust receiving portion 24, and a rotation preventing mechanism portion 25. , a rear bearing 26 and a connecting pin 25a. In this embodiment, the rear bearing 26 corresponds to the "shaft bearing" according to the invention.

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

A flange portion 21a1 formed in a flange shape is provided integrally with the eccentric shaft 21b at the one end portion of the drive shaft 21a. The other end of the drive shaft 21a has a reduced diameter and is rotatably supported by a front bearing 16 fitted to the support portion 12a1.

In this embodiment, a counterweight 27 for ensuring weight balance with respect to the movable scroll 3 is formed separately from the crankshaft 21 on the flange portion 21a1 formed integrally with the eccentric shaft 21b. The counterweight 27 is fixed to the flange portion 21a1 by a fastening member (not shown) such as a rivet. Specifically, the counterweight 27 is generally fan-shaped, and is positioned at a predetermined angle on the outer peripheral portion of the flange portion 21a1 at the one end of the drive shaft 21a so as to be substantially flush with the flange surface of the flange portion 21a1. It is fixed so that

Specifically, the eccentric shaft 21b has a circular cross-section about an axis eccentric to the rotation axis X of the drive shaft 21a, and extends toward the scroll unit 1 side.

In this embodiment, a circular hole 21b1 concentric with the rotation axis X is formed in the eccentric shaft 21b. 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 drive shaft 21a, but the center of the inner diameter of the eccentric shaft 21b is located on the rotation axis X of the drive shaft 21a. located above. In other words, the eccentric shaft 21b is formed in a cylindrical shape, and the center of the outer diameter of the cylinder is aligned with the inner diameter of the cylinder so that the first wrap 2b of the fixed scroll 2 and the second wrap 3b of the movable scroll 3 slide appropriately. is eccentric to the center of

In this embodiment, the eccentric shaft 21b is formed separately from the drive shaft 21a. Specifically, the hole diameter of the circular hole 21b1 of the eccentric shaft 21b is matched with the outer diameter of the drive shaft 21a, and penetrates the eccentric shaft 21b. The flange portion 21a1 is formed like a flange on the outer periphery of one end of the eccentric shaft 21b. The eccentric shaft 21b is fixed to the one end of the drive shaft 21a by press-fitting the one end of the drive shaft 21a into the circular hole 21b1 of the eccentric shaft 21b, leaving a housing area for the rear bearing 26. That is, a circular concave portion is formed at the one end portion (eccentric shaft side end portion) of the crankshaft 21 by the hole wall surface of the circular hole 21b1 and the end surface of the one end portion of the drive shaft 21a. A convex portion 24b of the thrust receiving portion 24, which will be described later, is inserted into this circular concave portion.

The turning bearing 22 is a bearing fitted with the eccentric shaft 21b, for example, a bearing fitted on the outer peripheral surface of the eccentric shaft 21b. In this embodiment, the turning bearing 22 consists of a cylindrical slide bearing. The slewing bearing 22 has a height approximately equal to the projection height of the flange portion 21a1 of the eccentric shaft 21b from the flange surface.

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

As shown in FIG. 4, connecting pins 25a, which will be described later, are inserted through a plurality (six locations in FIGS. 2 and 4) of the outer edge of the swinging member 23, which are equally spaced apart in the circumferential direction. A hole (hereinafter referred to as an insertion hole) 23b passes through. The rocking member 23 is formed such that regions between the insertion holes 23b on its outer edge are recessed radially inward. Thereby, the weight of the rocking member 23 is reduced. In addition, the depression of the outer edge of the swinging member 23, along with the through hole 24a of the thrust receiving portion 24, which will be described later, extends from the suction chamber H1 to the vicinity of the spiral outer end portions of the first wrap 2b and the second wrap 3b of the scroll unit 1. It functions as a coolant introduction passage for introducing a coolant (more specifically, a mixed fluid of coolant and lubricating oil) into the space H4 formed in . Therefore, the recess of the outer edge of the rocking member 23 sufficiently secures the coolant introduction passage, and the pressure loss in the coolant introduction passage can be easily reduced. A swivel bearing 22 is attached between the hole wall surface of the swivel bearing mounting hole 23a of the rocking member 23 and the outer peripheral surface of the eccentric shaft 21b. The slewing bearing 22 is, for example, press-fitted along either one of the outer peripheral surface of the eccentric shaft 21b and the hole wall surface of the slewing bearing mounting hole 23a. is slidably fitted along the other side of the wall surface of the hole. As a result, the swing member 23 is rotatably attached to the eccentric shaft 21b via the swivel bearing 22 about the axis of the eccentric shaft 21b (that is, the axis eccentric to the rotation axis X of the drive shaft 21a). installed. The swivel bearing 22 may be slidably fitted to both the outer peripheral surface of the eccentric shaft 21b and the hole wall surface of the swivel bearing mounting hole 23a.

As shown in FIG. 1, the thrust receiving portion 24 is provided between the second bottom plate 3a of the movable scroll 3 and the swinging member 23, and receives the thrust force of the movable scroll 3. As shown in FIG.

In this embodiment, the thrust receiving portion 24 is formed separately from the housing 10 . Specifically, the thrust receiving portion 24 is made of an appropriate material such as steel having better wear resistance than the material (eg, aluminum alloy) employed for the movable scroll 3, swinging member 23, housing 10, and the like. consists of The thrust receiving portion 24 is formed in a substantially disc shape having an outer diameter matching the inner diameter of the opening of the center housing 11 on the one end side (upper side in FIG. 1). The end surface of the outer edge portion of the thrust receiving portion 24 abuts 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, sandwiching the outer edge portion 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 in the circumferential direction with respect to the fixed scroll 2 is determined by suitable positioning means such as pins and pin holes (not shown). The space in the center housing 11 is divided by the thrust receiving portion 24 into a storage area for the scroll unit 1 (upper space in FIG. 1) and a storage area for main components of the drive mechanism 20 (lower space in FIG. 1). ) and Further, the crankshaft 21 has its play amount in the direction of the rotation axis X regulated by the thrust receiving portion 24 and the front bearing 16 .

In this embodiment, the slewing bearing 22 is positioned between the thrust receiving portion 24 and the counterweight 27 . In other words, the counterweight 27 is provided at the one end of the drive shaft 21a so that the slewing bearing 22 is positioned between the counterweight 27 and the thrust receiving portion 24. As shown in FIG.

As shown in FIGS. 1 and 5, the outer edge of the thrust receiving portion 24 is provided with a plurality of through holes 24a passing through the outer edge. In the present embodiment, the through-holes 24a are formed in a circular shape at a plurality of (six in FIG. 5) portions that are equally spaced apart in the circumferential direction of the outer edge of the thrust receiving portion 24 .

In this embodiment, a columnar protrusion 24b protrudes from the central portion of the end surface of the thrust receiving portion 24 on the swinging member side. The convex portion 24b has an outer diameter matching the inner diameter of the rear bearing 26. As shown in FIG. The protrusion height of the convex portion 24 b is generally matched with the height of the turning bearing 22 . A rear bearing 26 is fitted onto the outer peripheral surface of the convex portion 24b.

As shown in FIG. 1, a sealing member 19 is arranged on the other end surface (that is, the end surface on the thrust receiving portion side) that is the rear surface of the second bottom plate 3a of the orbiting scroll 3. As shown in FIG. The sealing member 19 maintains the airtightness of the back pressure chamber H3 defined between the back surface of the second bottom plate 3a and the end surface of the thrust receiving portion 24 on the movable scroll side. The back pressure chamber H3 has a gap height in the direction of the rotation axis X of the drive shaft 21a determined by the crushing margin of the seal member 19, and this gap height does not appear in FIG. 3 d of communication paths which connect the sealed space S and the back pressure chamber H3 are opened in the center part of the 2nd bottom plate 3a of the movable scroll 3. As shown in FIG.

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

Further, the through hole 24a of the thrust receiving portion 24 functions as a coolant introduction passage for introducing the coolant into the space H4, as described above. Since the through hole 24a communicates between the space H4 and the suction chamber H1, the pressure in the space H4 is equal to the pressure in the suction chamber H1 (intake chamber pressure).

As shown in FIGS. 1 and 6, a plurality of holes 3c are formed in the outer edge of the second bottom plate 3a of the movable scroll 3. As shown in FIG. 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 swinging member 23. As shown in FIG.

The rotation prevention mechanism 25 is a mechanism for preventing rotation of the movable scroll 3 . In the present embodiment, the rotation prevention mechanism 25 includes the plurality of through holes 24a passing through the outer edge of the thrust receiving portion 24, and the through holes 24a passing through the outer edge of the swing member 23 and the orbiting scroll 3. It is composed of a connecting pin 25a that connects with the outer edge of the second bottom plate 3a. The intermediate portion of the connecting pin 25 a is in sliding contact with the wall surface of the through hole 24 a to prevent the movable scroll 3 from rotating and to transmit the revolution driving force of the movable scroll 3 to the movable scroll 3 . That is, in the present embodiment, the connecting pin 25a has both the function of transmitting the revolution driving force and the function of preventing the movable scroll 3 from rotating. The through hole 23b in the swinging 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 diameters of the insertion hole 23b and the hole 3c, and is determined, for example, according to the required orbital turning radius of the movable scroll 3. The connecting pin 25a is made of, for example, a steel material like the thrust receiving portion 24, and is formed in a cylindrical shape with a diameter smaller than that of the through hole 24a. In this way, the intermediate portion of the connecting pin 25a is in sliding contact with the hole wall surface of the through hole 24a, thereby forming a rotation prevention mechanism 25 that prevents the movable scroll 3 from rotating. Further, the driving mechanism 20 including the rotation preventing mechanism portion 25 has a connecting pin 25a, and transmits the revolution driving force to the movable scroll 3 via the connecting pin 25a.

In this embodiment, one end of the connecting pin 25a is press-fitted into an insertion hole 23b, which is a hole formed in the outer edge of the swinging member 23, and the other end of the connecting pin 25a is inserted into the outer edge of the movable scroll 3. It is loosely fitted in the formed hole 3c. The movable scroll 3 is integrally coupled with the swinging member 23 by being connected with the swinging member 23 by 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 crankshaft 21, to the rotation axis. It is a bearing that supports rotatably around X. For example, the outer peripheral surface of the rear bearing 26 can slide against the inner peripheral surface of the circular hole 21b1, and the inner peripheral surface of the rear bearing 26 can slide against the outer peripheral surface of the convex portion 24b. , is fitted between the outer peripheral surface of the projection 24b and the inner peripheral surface of the circular hole 21b1. The rear bearing 26 is composed of, for example, a cylindrical slide bearing like the swivel bearing 22 . As a result, the one end (the eccentric shaft side end) of the crankshaft 21 is rotatably supported by the rear bearing 26, and the other end (the inverter side end) of the crankshaft 21 is fitted to the support portion 12a1. Both ends of the crankshaft 21 are rotatably supported within the housing 10 . Further, the one end of the crankshaft 21 is rotatably supported via the projection 24b of the thrust receiving portion 24. As shown in FIG. That is, in the present embodiment, the eccentric shaft 21b, which is the one end portion of the crankshaft 21, is supported by the thrust receiving portion 24 so as to be rotatable around the rotation axis X. As shown in FIG. The total radial clearance for the circular hole 21b1 and the projection 24b in the rear bearing 26 is larger than the total radial clearance for the swing member 23 and the eccentric shaft 21b in the turning bearing 22. set to be small.

The electric motor 30 is a drive source for the scroll unit 1, and generates rotational driving force for the drive shaft 21a. The electric motor 30 is provided in the housing 10 (specifically, the center housing 11) integrally with the drive shaft 21a. The electric motor 30 includes a rotor 31 and a stator core unit 32 arranged radially outside the rotor 31 . A three-phase AC motor, for example, is applied as the electric motor 30 . For example, direct current from a vehicle battery (not shown) is converted into alternating current by the inverter 40 and supplied to the electric motor 30 .

The rotor 31 is rotatably supported radially inside the stator core unit 32 via a drive shaft 21a fitted (for example, press-fitted) into a shaft hole formed in the radial center of the rotor 31 . When a magnetic field is generated in the stator core unit 32 by power supply from the inverter 40, rotational power acts on the rotor 31 to rotate the drive shaft 21a.

In the scroll type fluid machine 100 configured as described above, when the drive shaft 21a is rotationally driven by the electric motor 30, the eccentric shaft 21b moves along with the orbiting bearing 22 and the swinging member 23 to the axial center X of the fixed scroll 2. ', and this revolution driving force is transmitted to the movable scroll 3 via the connecting pin 25a. At this time, the orbiting scroll 3 is integrally connected with the swinging member 23 via the connecting pin 25a, and revolves integrally with the swinging member 23. As shown in FIG. The scroll-type fluid machine 100 compresses the refrigerant flowing into the closed space S between the fixed scroll 2 and the movable scroll 3 by this revolving motion.

Next, the flow of refrigerant in the scroll fluid machine 100 will be described.
Refrigerant from the low-pressure side of the refrigerant circuit is introduced into the suction chamber H1 through the suction port P1 and flows toward the swing member 23 while cooling the electric motor 30 . The coolant guided to the rocking member 23 side is then guided to the space H4 near the spiral outer end of the scroll unit 1 via the through hole 24a serving as the coolant introduction passage and the recess in the outer edge of the rocking member 23. . The refrigerant in the space H4 is taken into the sealed space S between the first wrap 2b and the second wrap 3b, and compressed in the sealed space S. The compressed refrigerant is discharged to the discharge chamber H2 via the discharge hole 2a1 and the one-way 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 that has flowed from the suction port P1 into the surroundings of the electric motor 30 in the housing 10 passes through the through hole 24a and flows through the first wrap 2b of the fixed scroll 2 and the second wrap of the movable scroll 3. It is led to a space H4 formed near the spiral outer end of 3b.

In the scroll-type fluid machine 100 according to the present embodiment, the drive mechanism 20 penetrates through the plurality of through holes 24a penetrating the outer edge of the thrust receiving portion 24, the outer edge of the swing member 23, and the second bottom plate of the orbiting scroll 3. It has a connecting pin 25a that connects with the outer edge of 3a. Therefore, when the drive shaft 21a is rotationally driven, the eccentric shaft 21b revolves around the axis X' of the fixed scroll 2 together with the orbiting bearing 22 and the swinging member 23, and this revolving driving force moves the connecting pin 25a. is transmitted to the movable scroll 3 via the In this way, the orbital driving force that causes the orbiting scroll 3 to revolve around the axis X′ of the fixed scroll 2 is transmitted by the connecting pin 25a. Therefore, the distortion of the second bottom plate 3a can be suppressed or prevented, thereby suppressing or preventing the deterioration of the performance of the scroll fluid machine.

In this way, it is possible to provide the scroll-type fluid machine 100 in which distortion of the second bottom plate 3a of the orbiting scroll 3 is suppressed or prevented and downsizing can be achieved.

Here, in the driving force transmission mechanism in the scroll-type fluid machine described in Patent Document 1, the orbiting bearing (corresponding to the orbiting bearing 22 according to the present embodiment) is located on the back side of the bottom plate of the orbiting scroll. It is provided inside the cylindrical boss portion which is cylindrically protruding from the center of the. In other words, the central area of the back surface of the bottom plate of the movable scroll is used as an area for mounting the orbiting bearing. For example, even if the outer diameter of the movable scroll can be reduced in order to reduce the size of the scroll-type fluid machine, it may be difficult to reduce the outer diameter of the orbiting bearing. In this case, even if the outer diameter of the bottom plate of the orbiting scroll is reduced, the ratio of the outer diameter of the cylindrical boss portion to the outer diameter of the bottom plate of the orbiting scroll becomes relatively large. Therefore, in the structure of the scroll-type fluid machine disclosed in Patent Document 1, when miniaturization is attempted, the sliding area between the thrust plate (corresponding to the thrust receiving portion 24 according to the present embodiment) and the orbiting scroll is reduced. A reduction in the sliding area increases the contact surface pressure between the thrust plate and the orbiting scroll. As a result, in the structure of the scroll-type fluid machine disclosed in Patent Document 1, when miniaturization is attempted, there is a possibility that the oil film will be easily cut off between the thrust plate and the bottom plate of the orbiting scroll, resulting in a decrease in reliability. There is

With respect to the decrease in reliability, in the scroll-type fluid machine 100 according to the present embodiment, the orbiting bearing 22 is provided not on the back surface of the second bottom plate 3a of the orbiting scroll 3, but on the thrust receiving portion 24 and the one end portion of the crankshaft 21. , the entire back surface of the second bottom plate 3 a of the movable scroll 3 can be used as a sliding surface with the thrust receiving portion 24 . Therefore, in the structure of the scroll-type fluid machine 100 according to the present embodiment, even when miniaturization is achieved by reducing the outer diameter of the second bottom plate 3a of the orbiting scroll 3, the back surface of the second bottom plate 3a of the orbiting scroll 3 is , the sliding area with the thrust receiving portion 24 can be sufficiently secured, and the reduction in size suppresses the occurrence of oil film breakage or the like between the thrust receiving portion 24 and the back surface of the second bottom plate 3a of the movable scroll 3. can be prevented.

Further, in the rotation prevention mechanism in the scroll-type fluid machine disclosed in Patent Document 1, the back surface of the thrust plate in which the slide hole is opened is in contact with the end surface of the front block. It is necessary to secure a space between the tip surface of the pin and the end surface (hole bottom) of the front block so that the tip surface does not contact the end surface (in other words, hole bottom) of the front block. Therefore, the space becomes a dead space, and there is a problem that the size of the fluid machine in the depth direction of the sliding hole (in other words, the direction of extension of the axis of the drive shaft) is increased by the amount of the space secured.

Regarding the size of the fluid machine, in the scroll-type fluid machine 100 of the present embodiment, the rotation prevention mechanism 25 is composed of the through hole 24a and the connecting pin 25a, and the intermediate portion of the connecting pin 25a is the hole of the through hole 24a. Since the rotation of the movable scroll 3 is prevented by sliding contact with the wall surface, the entire depth direction of the hole wall surface of the through hole 24a (that is, the entire thickness of the thrust receiving portion 24 in the present embodiment). Thus, the wall surface of the hole can be effectively used as a surface for sliding contact with the connecting pin 25a. Therefore, the conventional problem of dead space in the direction of hole depth can be eliminated, and the size of the housing can be reduced accordingly.

In this embodiment, the connecting pin 25a of the drive mechanism 20 has a function of preventing 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 eccentric shaft 21b that is the one end of the crankshaft 21 (in other words, the eccentric shaft side end of the crankshaft 21) is rotatably supported by the thrust receiving portion 24 around the rotation axis X. . That is, the bearing structure for the one end portion of the crankshaft 21 is configured using a portion of the thrust receiving portion 24 (specifically, the convex portion 24b) and a portion of the crankshaft 21 (the eccentric shaft 21b). Therefore, it is not necessary to form a conventional bearing support portion in the housing 10 in order to support the bearing on the one end side of the crankshaft 21. As a result, the structure of the housing 10 is simplified.

In this embodiment, a cylindrical projection 24b is projected from the central portion of the end face of the thrust receiving portion 24 on the swinging member side, and a circular hole 21b1 concentric with the rotation axis X is formed in the eccentric shaft 21b. It is configured to The driving mechanism 20 is fitted between the outer peripheral surface of the convex portion 24b and the inner peripheral surface of the circular hole 21b1, and is a rear bearing that rotatably supports the one end (the end on the eccentric shaft side) of the crankshaft 21. 26 are further included. In other words, the bearing structure for the one end portion of the crankshaft 21 is concentrated within a region inside the turning bearing 22 that rotatably supports the rocking member 23 . As a result, the bearing position of the one end (in other words, the end on the movable scroll side) of the crankshaft 21 can be set in the vicinity of the movable scroll 3, so that the compression reaction force generated when the refrigerant is compressed causes the crankshaft to move. The rotational moment load acting on the bearing engaged with the shaft 21 can be reduced, and the durability of the bearing is improved. In addition, since the main parts of the drive mechanism 20 (the swing member 23, the turning bearing 22, the eccentric shaft 21b, and the rear bearing 26) are concentrated in a region corresponding to the outer shape of the swing member 23, the housing 10 can be made smaller. The space inside the housing 10 can be effectively utilized.

In this embodiment, the electric motor 30 is provided in the housing 10 integrally with the drive shaft 21a, the scroll unit 1 compresses and discharges the refrigerant from the closed space S, and the housing 10 has an intake port P1 into which the refrigerant flows. It is configured to be formed. Refrigerant that has flowed from the suction port P1 into the surroundings of the electric motor 30 in the housing 10 passes through the through hole 24a and flows into the space H4 formed near the spiral outer end portions of the first wrap 2b and the second wrap 3b. is led to In other words, the through hole 24a functions not only as the rotation prevention mechanism 25, but also as a refrigerant introduction passage for introducing the refrigerant from the suction chamber H1 to the space H4. Therefore, it is not necessary to separately form the coolant introduction passage in the housing 10 or the like, and the productivity of the scroll type fluid machine 100 can be improved. Further, the recess on the outer edge of the rocking member 23 also functions as a coolant introduction passage, and has the same effect as the through hole 24a.

In this embodiment, one end of the connecting pin 25a is press-fitted into an insertion hole 23b formed in the outer edge of the swinging member 23, and the other end of the connecting pin 25a is inserted into a hole 3c formed in the outer edge of the movable scroll 3. is loosely fitted in That is, play (a gap between the outer surface of the pin and the hole wall surface of the hole 3c) is eliminated on the driving side (swing member 23 side) of the connecting pin 25a, and play is eliminated on the driven side (moving scroll 3 side) of the connecting pin 25a. are provided. As a result, manufacturing tolerances of the first wrap 2b, the second wrap 3b, etc. are absorbed by the play on the driven side of the connecting pin 25a.

In this embodiment, the eccentric shaft 21b is formed separately from the drive shaft 21a. As a result, the crankshaft 21 can be manufactured more easily than when the eccentric shaft 21b is integrally formed with the drive shaft 21a. In other words, in the case of integral formation, for example, the eccentric shaft 21b must be formed by a machine with a high time charge, such as a forming machine. As a result, manufacturing costs can be reduced.

In this embodiment, the thrust receiving portion 24 is formed separately from the housing 10 . As a result, the thrust receiving portion 24, which requires high wear resistance, can be made of a material with wear resistance taken into consideration or subjected to surface treatment, etc., and the housing 10 can be made of a material that prioritizes weight reduction.

In this embodiment, the counterweight 27 is formed separately from the crankshaft 21 . Thereby, the manufacturing cost of the counterweight 27 can be reduced. Further, in the conventional scroll-type fluid machine described in Patent Document 1, the counterweight is arranged in a narrow space in the radial direction of the housing between the movable scroll and the bearing on the movable scroll side of the crankshaft. Therefore, it was necessary to shorten the size of the counterweight in the radial direction. Therefore, the position of the center of gravity of the counterweight becomes close to the rotation axis of the drive shaft, and as a result, the weight of the counterweight has to be increased in order to secure the required weight balance. On the other hand, in this embodiment, the counterweight 27 is provided so that the turning bearing 22 is positioned between the counterweight 27 and the thrust receiving portion 24 at the one end of the drive shaft 21a. Therefore, the counterweight 27 can be arranged in a wide space between the outer peripheral portion of the one end of the drive shaft 21a and the inner peripheral surface of the housing 10 (center housing 11). It can be kept away from the rotation axis X of the drive shaft 21a more than before. Therefore, the counterweight 27 can be made lighter than the conventional counterweight.

Next, a second embodiment of the invention will be described with reference to FIGS. 7 to 11. FIG.
FIG. 7 is a cross-sectional view of a scroll-type fluid machine showing a second embodiment of the invention. FIG. 8 is a cross-sectional view of the main part taken along line BB in FIG. FIG. 9 is a partial front view of the crankshaft 21, FIG. 10 is a partial front view of the eccentric shaft 21b, and FIG. 8, the rear bearing 26 and the convex portion 24b of the thrust receiving portion 24 are omitted. The same reference numerals are given to the same elements as in the first embodiment, and the parts different from the first embodiment will be described.

In the first embodiment, the turning bearing 22 and the rear bearing 26 are composed of slide bearings. On the other hand, in the second embodiment, the turning bearing 22 and the rear bearing 26 are rolling bearings, as shown in FIGS.

In the first embodiment, the eccentric shaft 21b is composed of one component. On the other hand, in the second embodiment, as shown in FIGS. 7 to 10, the eccentric shaft 21b is composed of two parts, an eccentric bushing 21b' and a collar 21b''. It has a large-diameter portion and a small-diameter portion smaller than the large-diameter portion, into which the one end of the drive shaft 21a is press-fitted, and the large-diameter portion accommodates the rear bearing 26. The eccentric bushing 21b' is press-fitted to the one end of the drive shaft 21a, and a collar 21b'' is fitted to the outside of the eccentric bush 21b', so that one end of the drive shaft 21a in the axial direction is rotated with respect to the rotation axis X. An eccentric shaft 21b is provided eccentrically.

Specifically, the eccentric bushing 21b′ is provided at the one end of the drive shaft 21a with respect to the rotation axis X of the drive shaft 21a, and is cylindrically shaped along the axis eccentric to the rotation axis X. It is stretched. As shown in FIG. 9, the outer surface of the eccentric bushing 21b' is formed with notched surfaces 21b'1 that are notched so as to face each other in parallel. That is, the outer cylindrical surface of the eccentric bushing 21b' is composed of a flat notch surface 21b'1 facing each other and an arc-shaped arc surface 21b'2 facing each other. is located on an axis eccentric to the rotation axis X of the drive shaft 21a. A circular hole 21b1 concentric with the rotation axis X is formed in the eccentric bushing 21b', and a flange portion 21a1 is formed like a collar on the outer circumference of one end of the eccentric bushing 21b'.

The collar 21b'' has a circular cross-section about an axis eccentric to the rotation axis X of the drive shaft 21a. The collar 21b'' is, as shown in FIG. has a shape corresponding to the cylindrical outer surface of the eccentric bushing 21b'. That is, the inner surface of the collar 21b'' is composed of a flat engaging surface 21b''1 facing each other and a circular arc surface 21b''2 facing each other. , the collar 21b'' revolves around the axis X' of the fixed scroll 2 together with the eccentric bushing 21b', the orbiting bearing 22, and the oscillating member . The clearance between the cutout surface 21b′1 of the eccentric bushing 21b′ and the engaging surface 21b″1 of the collar 21b″ is defined by the arc surface 21b′2 of the eccentric bushing 21b′ and the arc surface 21b″2 of the collar 21b″. is set to about 1/5 to 1/20 of the clearance between . Therefore, the circumferential movement of the collar 21b'' with respect to the eccentric bushing 21b' is restricted by the cutout surface 21b'1 and the engaging surface 21b''1. In addition, the clearance between the arc surface 21b'2 and the arc surface 21b''2 ensures play against the accumulated manufacturing tolerance of each component, and when an excessive compression reaction force occurs during liquid compression. For example, when a compression reaction force acts on the orbiting scroll 3 in the direction indicated by arrow C in FIG. 23. At this time, the engaging surface 21b''1 of the collar 21b'' turns the eccentric bushing 21b' in the direction of increasing the orbital turning radius of the orbiting scroll 3 (the direction indicated by the hollow arrow D in FIG. 8). The movable scroll 3 slides along the cutout surface 21b'1 by the clearance between the arcuate surface 21b'2 and the arcuate surface 21b''2, and the orbiting scroll 3 is biased together with the swing member 23 in the direction of this sliding movement. be done.

Thus, in the second embodiment, the eccentric shaft 21b includes the eccentric bushing 21b' provided at the one end of the drive shaft 21a eccentrically with respect to the rotation axis X, the outer peripheral surface of the eccentric bushing 21b' and the turning bearing. 22. The collar 21b'' is prevented from rotating with respect to the eccentric bushing 21b' and has a predetermined position with respect to the eccentric bushing 21b'. is attached to the outer peripheral surface of the eccentric bushing 21b' so as to allow movement by a predetermined clearance in the radial direction (direction indicated by arrow D).

In the first embodiment, the counterweight 27 is formed separately from the crankshaft 21 . In contrast, in the second embodiment, the counterweight 27 is formed integrally with a portion of the crankshaft 21 as shown in FIG. Specifically, the counterweight 27 is formed integrally with the collar 21b'' that constitutes the eccentric shaft 21b of the crankshaft 21. More specifically, the counterweight 27 is formed on the outer peripheral portion of the collar 21b'' on the flange portion 21a1 side. is formed at a predetermined angular portion in Also, the counterweight 27 is arranged between the flange portion 21 a 1 and the swing bearing 22 and the swing member 23 . The flange portion 21a1 and the thrust receiving portion 24 of the counterweight 27 and the swinging member 23 regulate the amount of play and the amount of inclination in the direction of the rotation axis X of the drive shaft 21a.

Further, as shown in FIG. 11, the turning bearing mounting hole 23a of the swinging member 23 has a large opening with an inner diameter matching the outer diameter of the turning bearing 22. As shown in FIG.

In the scroll-type fluid machine 100 according to the second embodiment as well, the revolution driving force for causing the movable scroll 3 to revolve around the axis X′ of the fixed scroll 2 is transmitted by the connecting pin 25a. Distortion of the second bottom plate 3a of the orbiting scroll 3 due to the transmission structure is suppressed or prevented, thereby suppressing or preventing performance degradation of the scroll fluid machine. In addition, the conventional problem of dead space in the hole depth direction can be eliminated, and the size of the housing can be reduced accordingly.

In addition, in each embodiment, although the rotation prevention mechanism part 25 shall be comprised by the through-hole 24a and the connection pin 25a, it is not restricted to this. For example, as the rotation prevention mechanism 25, an Oldham coupling method may be adopted, 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.

12 to 15 are diagrams for explaining an example of a scroll-type fluid machine 100 that employs the Oldham's coupling method. FIG. 12 is a cross-sectional view of a scroll-type fluid machine 100 that employs the Oldham's coupling method. 13 is a front view of the rocking member 23, FIG. 14 is a front view of the thrust receiving portion 24, and FIG. 15 is a front view of an Oldham ring 28, which will be described later. The same reference numerals are given to the same elements as in the first embodiment, and only the parts different from the first embodiment will be described. The scroll type fluid machine 100 adopting the Oldham's coupling method will be described below as a modification of the scroll type fluid machine 100 of the first embodiment, but it is also adopted for the scroll type fluid machine 100 of the second embodiment. be able to.

The rotation prevention mechanism 25 includes, for example, a pair of first key grooves 23c, 23c formed in the swing member 23, a pair of second key grooves 24c, 24c formed in the thrust receiving portion 24, and an Oldham ring 28. It is composed of As shown in FIGS. 12 and 13, a large-diameter concave portion 23d having a diameter larger than that of the orbiting bearing mounting hole 23a is formed in the end surface of the swinging member 23 on the thrust receiving portion side. The Oldham ring 28 is accommodated in the large-diameter recess 23d. The pair of first key grooves 23c, 23c are formed in a row on the bottom surface of the large-diameter recess 23d of the swing member 23. As shown in FIG. As shown in FIG. 14, the pair of second key grooves 24c, 24c are formed in a row on the outer edge of the end face of the thrust receiving portion 24 on the rocking member side, avoiding the opening position of the through hole 24a. It is When the swing member 23 and the thrust receiving portion 24 are assembled, the pair of first key grooves 23c, 23c of the swing member 23 and the pair of second key grooves 24c, 24c of the thrust receiving portion 24 are: arranged perpendicular to each other. As shown in FIG. 15, the Oldham ring 28 includes an annular ring 28a having a thickness corresponding to the depth of the large-diameter recess 23d, a pair of first key portions 28b, 28b, and a pair of second key portions 28c. , 28c. The pair of first key portions 28b, 28b protrude in a row from one end face of the ring 28a in the thickness direction, and are fitted into the pair of first key grooves 23c, 23c. The pair of second key portions 28c, 28c protrude from the other end face in the thickness direction of the ring 28a so as to be perpendicular to the pair of first key portions 28b, 28b and to be aligned in a row. It is fitted into the key grooves 24c, 24c. Rotational motion of the swinging member 23 is restricted (prevented) by a pair of first key portions 28b, 28b and a pair of second key portions 28c, 28c. Since the orbiting scroll 3 is integrally connected via the connecting pin 25a to the oscillating member 23 whose rotation is prevented, the rotation of the orbiting scroll 3 is prevented.

In each embodiment, the bearing structure for the one end portion side (eccentric shaft side) of the crankshaft 21 consists of a convex portion 24b of the thrust receiving portion 24, a circular hole 21b1 in the eccentric shaft 21b, and the one end portion of the drive shaft 21a. and the rear bearing 26 between the convex portion 24b and the circular recess. For example, the thrust receiving portion 24 is provided with a circular concave portion, the end surface of the eccentric shaft 21b is provided with a convex portion, and the rear bearing 26 is provided between the circular concave portion of the thrust receiving portion 24 and the convex portion of the eccentric shaft 21b. may be Moreover, although the said circular recessed part shall be formed by the hole wall surface of the circular hole 21b1, and the end surface of the said one end part of the drive shaft 21a, it is not restricted to this. Although not shown, the eccentric shaft 21b may be provided with a circular recess concentric with the rotation axis X instead of the circular hole 21b1.

Further, in each embodiment, the bearing structure for the one end portion side (eccentric shaft side) of the crankshaft 21 is configured to be integrated within a region inside the turning bearing 22 that rotatably supports the rocking member 23. However, it is not limited to this. may be provided so as to protrude from the inner peripheral surface of the housing 10 (center housing 11). Also, one end of the connecting pin 25a is press-fitted into the insertion hole 23b of the swinging member 23, and the other end of the connecting pin 25a is loosely fitted into the hole 3c of the movable scroll 3. However, the present invention is not limited to this. Both ends of the connecting pin 25a may be press-fitted into corresponding holes (insertion hole 23b, hole 3c), or may be fitted with appropriate play. Furthermore, the eccentric shaft 21 b may be formed integrally with the drive shaft 21 a, and the thrust receiving portion 24 may be formed integrally with the housing 10 . Moreover, although the circular hole 21b1 penetrating the eccentric shaft 21b is provided to accommodate the rear bearing 26, the present invention is not limited to this. In addition to the through hole 24a, a hole may be formed through the thrust receiving portion 24 to communicate between the suction chamber H1 and the space H4. As a result, the number of refrigerant introduction passages is increased, pressure loss is further reduced, and as a result, power consumption is further reduced.

Further, in each embodiment, the scroll type fluid machine 100 has been described as an example of a so-called inverter integrated type, but the scroll type fluid machine 100 is not limited to this and may be separate from the inverter 40 . Moreover, although the electric motor 30 is built in, the electric motor 30 may be provided outside the housing 10 . Although the electric motor 30 is used as the drive source, the present invention is not limited to this, and may be configured to transmit rotational power from the engine of the vehicle to the drive shaft 21a. Further, in each embodiment, the fluid is assumed to be a coolant, but the fluid is not limited to this, and an appropriate fluid can be applied.

Although the preferred embodiments of the present invention have been described above, the present invention is not limited to the above embodiments and modifications, and various modifications and changes are possible based on the technical idea of the present invention.

2... fixed scroll, 2a... first bottom plate (bottom plate), 2b... first wrap (wrap), 3... movable scroll, 3a... second bottom plate (bottom plate), 3b... second wrap (wrap), 3c... hole, DESCRIPTION OF SYMBOLS 10... Housing 20... Drive mechanism 21... Crankshaft 21a... Drive shaft 21b... Eccentric shaft 21b1... Circular hole 22... Turning bearing 23... Rocking member 23b... Insertion hole (hole) 24... Thrust receiving portion 24a through hole 24b convex portion 25 rotation prevention mechanism portion 25a connecting pin 26 rear bearing (shaft bearing) 27 counterweight 30 electric motor 100 scroll fluid Machine H4 Space P1 Suction port S Sealed space X Rotation axis X' Fixed scroll axis

Claims (8)

a fixed scroll and a movable scroll, each having a bottom plate and a spiral wrap erected on the bottom plate and engaged with each other; a drive mechanism for transmitting revolution driving force is provided in the housing, the orbiting scroll revolving while being in contact with the fixed scroll and forming a sealed space between the fixed scroll and the fixed scroll whose volume changes as it revolves. A scroll-type fluid machine,
The drive mechanism is
A crankshaft having a drive shaft rotatably driven around a rotation axis aligned with the axis of the fixed scroll, and an eccentric shaft provided at one end in the axial direction of the drive shaft eccentrically with respect to the rotation axis. When,
a slewing bearing fitted with the eccentric shaft;
an annular oscillating member fitted around the outer peripheral surface of the orbiting bearing;
a thrust receiving portion provided between the bottom plate of the orbiting scroll and the oscillating member for receiving the thrust force of the orbiting scroll;
a rotation prevention mechanism that prevents rotation of the orbiting scroll;
including
The drive mechanism has a connecting pin that passes through a plurality of through holes penetrating the outer edge of the thrust receiving portion and connects between the outer edge of the swing member and the outer edge of the bottom plate of the orbiting scroll. and transmitting the orbital driving force to the orbiting scroll via the connecting pin. The through-hole is circularly opened,
the connecting pin is formed to have a smaller diameter than the through hole,
2. The mechanism according to claim 1, wherein the rotation-preventing mechanism comprises the through-hole and the connecting pin, and an intermediate portion of the connecting pin is in sliding contact with a wall surface of the through-hole to prevent rotation of the orbiting scroll. A scroll-type fluid machine as described. 3. The scroll type fluid machine according to claim 1, wherein said eccentric shaft, which is one end of said crankshaft, is rotatably supported by said thrust receiving portion about said rotation axis. A columnar projection is provided at a central portion of the end surface of the thrust receiving portion on the side of the swinging member,
The eccentric shaft is configured to have a circular hole or circular recess concentric with the rotation axis,
The drive mechanism is fitted between the outer peripheral surface of the convex portion of the thrust receiving portion and the inner peripheral surface of the circular hole or the circular concave portion of the eccentric shaft, and rotatably rotates the one end of the crankshaft. 4. The scroll type fluid machine according to claim 3, further comprising a supporting shaft bearing. An electric motor for generating rotational driving force of the drive shaft is provided in the housing integrally with the drive shaft,
the fixed scroll and the orbiting scroll compress and discharge a fluid from the closed space;
The housing is formed with a suction port into which the refrigerant as the fluid flows,
Refrigerant that has flowed from the suction port into the surroundings of the electric motor in the housing is guided through the through hole to a space formed in the vicinity of the spiral outer end portions of the wraps of the movable scroll and the fixed scroll. The scroll type fluid machine according to any one of claims 1 to 4, wherein the scroll type fluid machine is one end of the connecting pin is press-fitted into a hole formed in the outer edge of the swinging member,
6. The scroll type fluid machine according to claim 1, wherein the other end of said connecting pin is loosely fitted in a hole formed in said outer edge of said orbiting scroll. The eccentric shaft is cylindrical and is fitted between an eccentric bush provided at the one end of the drive shaft eccentrically with respect to the rotation axis, and an outer peripheral surface of the eccentric bush and an inner peripheral surface of the swivel bearing. is composed of the color of
The collar is attached to the outer peripheral surface of the eccentric bushing so as to prevent rotation with respect to the eccentric bushing and to allow movement of the eccentric bushing in a predetermined radial direction by a predetermined clearance. The scroll type fluid machine according to any one of items 1 to 6. A counterweight for ensuring weight balance with respect to the orbiting scroll is provided at the one end of the drive shaft so that the orbiting bearing is positioned between the counterweight and the thrust receiving portion. Item 8. The scroll type fluid machine according to any one of items 1 to 7.

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