JP6335542B2 - Scroll compressor - Google Patents

Description

  The present invention relates to a rotation prevention mechanism for a scroll compressor.

  The scroll compressor includes a fixed scroll and a turning scroll. Both the fixed scroll and the orbiting scroll are provided with a spiral wrap on one side of a disk-shaped end plate. Such a fixed scroll and the orbiting scroll are made to face each other in a state where the lap is engaged, and the orbiting scroll is caused to perform a revolving orbiting operation with respect to the fixed scroll. And the volume of the compression space formed between both scrolls is decreased with the turning of the orbiting scroll, thereby compressing the fluid in the space.

  A crankpin type rotation prevention mechanism is known as a mechanism for preventing the rotation of the orbiting scroll. The crankpin type anti-rotation mechanism supports the crankpin by a bearing, and provides a predetermined clearance between the bearing and the bearing housing, or between the crankpin and the bearing, and between the bearing and the bearing housing, or the crankpin. An elastic member that fills the clearance, typically an O-ring, is interposed between the pin and the bearing (for example, Patent Document 1 and Patent Document 2). There are several reasons for adopting such a configuration in which a clearance is provided and an elastic member is interposed therein, and one of them is the thermal expansion of the orbiting scroll caused by the compression of the fluid. That is, damage to the orbiting scroll due to thermal expansion is prevented by absorbing the displacement of the crankpin in the radial direction of the orbiting scroll due to the thermal expansion of the orbiting scroll by the O-ring that is an elastic body.

Japanese Patent Laid-Open No. 11-82328 JP 2003-269101 A

However, in the above-described conventional technique in which the O-ring is interposed, since the predetermined clearance is provided in the entire circumferential direction corresponding to the O-ring, the clearance is not only in the radial direction of the orbiting scroll but also in the circumferential direction. Will exist. Therefore, if the crank pin is displaced in the circumferential direction, the orbiting scroll is displaced in the circumferential direction along with this displacement, and a twist occurs between the orbiting scroll and the fixed scroll. Due to this twist, the fluid cannot be compressed normally, and the wrap of the orbiting scroll and the wrap of the fixed scroll may come into strong contact with each other and may be damaged.
The present invention has been made based on such a problem, and an object of the present invention is to provide a scroll compressor capable of absorbing the displacement of the orbiting scroll due to thermal expansion and preventing the orbiting scroll from being twisted.

The scroll compressor of the present invention, which has been made for this purpose, is combined to form a compression space for reciprocating orbiting with respect to the fixed scroll and the fixed scroll and compressing fluid between the fixed scroll and the fixed scroll. A turning scroll and a rotation prevention mechanism of the turning scroll.
The rotation preventing mechanism includes a pin crank having a first pin and a second pin, a first bearing that is supported by a bearing box integral with the orbiting scroll, and supports the first pin, and a second bearing provided in the vicinity of the bearing box. A second bearing that is held in the bearing housing space or the fixed scroll and supports the second pin.
In this rotation prevention mechanism, when the allowable displacement amount of the first pin in the radial direction of the orbiting scroll is δr and the allowable displacement amount of the first pin in the circumferential direction of the orbiting scroll is δθ,
δθ <δr Formula (1)
It is characterized by satisfying. In addition to the above features, the scroll compressor of the present invention is such that the fixed scroll wrap and the orbiting scroll wrap each have a step at the tooth tip and the root, so that the outer peripheral side is closer to the inner side. Is characterized by being tall.

  According to the scroll compressor of the present invention, since the rotation prevention mechanism satisfies the above formula (1), the displacement in the circumferential direction can be kept small. Therefore, according to the scroll compressor of the present invention, it is possible to absorb the displacement of the crankpin in the radial direction due to the thermal expansion of the orbiting scroll and to prevent the orbiting scroll from being twisted.

In the scroll compressor of the present invention, to achieve the equation (1), the opening of the bearing housing for holding the bearings has a major axis in the radial direction, and a shape having a minor axis in the circumferential direction . In this form state, it does not interfere with the provision of the elastic member such as an O-ring.

According to the present invention, the allowable displacement of the first pin in the radial direction can be increased, while the allowable displacement of the first pin in the circumferential direction can be decreased.
Therefore, the scroll compressor according to the present invention can absorb the displacement of the crankpin in the radial direction due to the thermal expansion of the orbiting scroll, and can prevent the orbiting scroll from being twisted .

  According to the scroll compressor of the present invention, in addition to permitting the displacement of the crankpin in the radial direction due to the thermal expansion of the orbiting scroll, it is possible to prevent the orbiting scroll from being twisted.

It is a longitudinal cross-sectional view which shows the principal part of the scroll compressor which concerns on 1st Embodiment of this invention. FIG. 2 is a cross-sectional view including a first element portion of a rotation prevention mechanism of the scroll compressor of FIG. 1. (A) is the figure which extracted and showed only the part of the 1st element of FIG. 2, (b) is the IIIb-IIIb arrow directional cross-sectional view of (a), (c) is IIIc of (a). FIG. (A) is a perspective view which shows the circumference | surroundings of the wrap of a fixed scroll from the front side, (b) is a perspective view which shows the circumference | surroundings of the wrap of a turning scroll from the front side. It is a figure corresponding to Drawing 3 showing the scroll compressor concerning a 2nd embodiment of the present invention. It is a figure corresponding to Drawing 3 showing a scroll compressor concerning a 3rd embodiment of the present invention.

  Hereinafter, the present invention will be described in detail based on embodiments shown in the accompanying drawings.

[First Embodiment]
As shown in FIGS. 1 and 2, the scroll compressor 1 according to this embodiment includes a housing 10 that forms an outer shell of the scroll compressor 1, a fixed scroll 20 that is fixed to the housing 10, and a swivel inside the housing 10. A revolving scroll 30 that can be accommodated is provided as a main component. These main components are made of a metal material such as an aluminum alloy or an iron alloy.
The scroll compressor 1 is a scroll compressor called a 3D scroll (registered trademark) that can obtain a high compression ratio by compressing a fluid not only in a circumferential direction but also in a height direction.

[Housing 10]
As shown in FIG. 1, the housing 10 is a hermetic container including a first housing 10a and a second housing 10b.
The first housing 10 a is fixed to the fixed scroll 20 and accommodates the cooling fins 24 of the fixed scroll 20 inside. The first housing 10 a includes a discharge port 12 that discharges the compressed fluid discharged from the discharge port 21 e of the fixed scroll 20 toward the outside.
The second housing 10b houses and holds the orbiting scroll 30, the rotation prevention mechanism 40, and the drive shaft 50 in the housing chamber 11b. The second housing 10 b includes a storage chamber 11 c that stores the second element 45 of the rotation prevention mechanism 40 and a storage chamber 11 d that stores the drive shaft 50 and the main bearing 54 inside the storage chamber 11 b.

[Fixed scroll 20]
As shown in FIG. 1, the fixed scroll 20 includes an end plate 21 formed in a substantially disc shape, a spiral wrap 22 provided on one surface side of the end plate 21, and the other surface of the end plate 21. The cooling fin 24 provided in the side and the outer peripheral wall 26 surrounding the outermost periphery of the fixed scroll 20 are provided, and are integrally formed by casting, for example, an aluminum alloy. The outer peripheral wall 26 is provided with a suction port 27 for sucking a fluid to be compressed. Further, the outer peripheral wall 26 is exposed to the outside and constitutes a part of the housing 10. In the fixed scroll 20, the side on which the wrap 22 is provided is referred to as the front, and the side on which the cooling fins 24 are provided is referred to as the back.

The 3D type scroll compressor 1 is provided with a low step portion 21a and a high step portion 21b on the end plate 21 so that the height of the wrap 22 is lower on the inner peripheral side than on the outer peripheral side. The wrap 22 formed on 21a is tall, and the wrap 22 formed on the high step portion 21b is short. A step at the boundary between the low step portion 21 a and the high step portion 21 b also appears on the back surface of the end plate 21.
The tip of the wrap 22 is provided with a tip seal 23 having a self-lubricating property that contacts the front side of the end plate 31 of the orbiting scroll 30 and seals the compression chamber.

  The end plate 21 is formed with a discharge port 21e penetrating the front and back, and the fluid compressed by the fixed scroll 20 and the orbiting scroll 30 is discharged from the discharge port 12 to the outside through the discharge port 21e.

  A plurality of cooling fins 24 are provided on the back surface of the end plate 21, and outside air flowing from openings (not shown) formed in the housing 10 passes through the cooling fins 24 to cool the fixed scroll 20. . In the present embodiment, the plurality of plate-like cooling fins 24 are formed in the same direction, but for example, the plurality of cooling fins 24 can be provided radially from the center of the end plate 21. The same applies to the orbiting scroll 30.

[Swivel scroll 30]
As shown in FIG. 1, the orbiting scroll 30 includes an end plate 31 formed in a substantially disc shape, a spiral wrap 32 provided on one surface side of the end plate 31, and the other surface of the end plate 31. The cooling fin 34 is provided on the side, and is integrally formed by casting, for example, an aluminum alloy. In the fixed scroll 20, the side where the wrap 32 is provided is referred to as the front, and the side where the cooling fins 34 are provided is referred to as the back.

The wrap 32 of the orbiting scroll 30 corresponds to the wrap 22 of the fixed scroll 20 and is formed such that the height of the spine is lower on the inner peripheral side than on the outer peripheral side. The end plate 31 is provided with a low step portion 31a and a high step portion 31b. The wrap 32 formed on the low step portion 31a is tall and the wrap 32 formed on the high step portion 21b is tall. Low. In addition, the level | step difference of the boundary of the low step part 31a and the high step part 31b has also appeared on the back surface of the end plate 31, and the recessed groove 31c which recedes toward the front is formed in the said part.
The tip of the wrap 32 is provided with a tip seal 33 having a self-lubricating property that contacts the front side of the end plate 21 of the fixed scroll 20 and seals the compression chamber.

  A plurality of cooling fins 34 are provided on the back surface of the end plate 31, and the orbiting scroll 30 is cooled by the outside air flowing from the openings (not shown) formed in the housing 10 passing through the cooling fins 34. . The plurality of plate-like cooling fins 34 are formed in the same direction.

The orbiting scroll 30 includes an orbiting plate 35 that is fixed to the front end side of the cooling fin 34.
The swivel plate 35 is provided with a boss 36 that houses and fixes a bearing 37 at the center. The bearing 37 held by the boss 36 supports the eccentric shaft 53 of the drive shaft 50.
In addition, the swivel plate 35 includes three bosses 38 that accommodate the first elements 41 of the rotation prevention mechanism 40 at regular intervals in the circumferential direction, as shown in FIG.

[Rotation prevention mechanism 40]
The rotation prevention mechanism 40 is a pin crank type rotation prevention mechanism, and includes a first element 41 and a second element 45. The scroll compressor 1 includes three rotation prevention mechanisms 40.
The first element 41 includes a bearing (first bearing) 42. The bearing 42 includes, for example, a ball bearing including an inner ring, an outer ring, and a spherical rolling element provided between the inner ring and the outer ring. A crank pin (first pin) 43 is fitted to the inner ring of the bearing 42 and constitutes a first element 41 together with the bearing 42. The first element 41 is accommodated inside a boss 38 of the turning plate 35, and this boss 38 functions as a bearing box of the bearing 42. Although not shown, an elastic member such as an O-ring can be provided between the bearing 42 and the crank pin 43 or on the outer periphery of the bearing 42. The same applies to the second element 45.
The second element 45 has the same configuration as the first element 41, and includes a bearing (second bearing) 46 and a crank pin (second pin) 47 inserted into the inner ring of the bearing 46. Yes. The second element 45 is accommodated and held in the accommodation chamber 11 c of the housing 10.

  The crank pin 43 of the first element 41 and the crank pin 47 of the second element 45 are integrally connected via an eccentric shaft 44, and the crank pin 43, the crank pin 47 and the eccentric shaft 44 are integrated with each other. Configure.

As shown in FIGS. 2 and 3, the boss 38 has an inner wall 38a. The inner wall 38a regulates the amount and direction of displacement of the bearing 42. Opening of the inner wall 38a, unlike the perfect circle has a long diameter D _L in the radial direction of which is part pivot plate 35 of the orbiting scroll 30, an oval shape having a minor axis D _S in the circumferential direction of the pivot plate 35 I am doing. On the other hand, the bearing 42 has a perfect circle (diameter D). Therefore, as shown in FIG. 3, assuming that the center of the region surrounded by the inner wall 38a coincides with the center of the bearing 37, the radial displacement allowance δr and the circumferential displacement allowance δθ are as follows. It is.
δr = (D _L −D ) / 2, δθ = (D _S −D ) / 2
_Here, since it is D L> _{D S,} the [delta] r> .delta..theta. That is, the boss 38 and the bearing 42 have anisotropy that the allowable displacement amount of the bearing 42 (crank pin 47) is large in the radial direction of the turning plate 35 and small in the circumferential direction of the turning plate 35 . .

[Drive shaft 50]
The drive shaft 50 transmits a rotational drive force of a drive source (not shown) such as an electric motor to the orbiting scroll 30.
As shown in FIG. 1, the drive shaft 50 has a connection end 51 connected to a drive source on one end side, and an eccentric shaft 53 held on a bearing 37 held on the swivel plate 35 on the other end. It has been.
The drive shaft 50 is rotatably supported on the housing 10 by two bearings of a main bearing 54 and a sub bearing 55. The main bearing 54 supports the drive shaft 50 in the vicinity of the eccentric shaft 53, and the auxiliary bearing 55 supports the drive shaft 50 in the vicinity of the connection end 51.

[Operation of scroll compressor 1]
Next, the operation of the scroll compressor 1 having the above configuration is as follows.
When the drive shaft 50 rotates according to the rotation of a drive source (not shown), the orbiting scroll 30 starts a revolving orbiting motion. Then, the fluid sucked from the suction port 27 is compressed in the crescent-shaped compression space formed by the wrap 22 and the wrap 32 and is discharged from the discharge port 12 provided in the central portion.
While the scroll compressor 1 is operating, the rotation prevention mechanism 40 prevents the orbiting scroll 30 from rotating.

[Effect of scroll compressor 1]
Next, the effect of the scroll compressor 1 will be described.
Since the temperature rises when the fluid is compressed, the fixed scroll 20 and the orbiting scroll 30 are exposed to a high temperature and thermally expanded while the scroll compressor 1 is driven. In the scroll compressor 1, the rotation prevention mechanism 40 of the orbiting scroll 30 has a large allowable displacement amount of the bearing 42 in the radial direction of the orbiting plate 35 that is a part of the orbiting scroll 30, and the circumferential direction of the orbiting plate 35. It has a small anisotropy. Therefore, even if the orbiting scroll 30 is thermally expanded, the radial displacement of the bearing 42 is absorbed in the range of 2δr at the maximum. On the other hand, since the allowable displacement amount δθ in the circumferential direction is smaller than the allowable displacement amount δr in the radial direction, the amount of displacement of the bearing 42 in the circumferential direction can be kept small. Therefore, it is possible to suppress the turning scroll 30 from being twisted with respect to the fixed scroll 20.

  Next, the scroll compressor 1 is a 3D type compressor, and the fluid is compressed not only in the circumferential direction but also in the height direction, so that a high compression ratio can be obtained. However, in this 3D type compressor, the fixed scroll 20 includes a low step portion 21a and a high step portion 21b, and as shown in FIG. 4A, the tip (tooth tip) of the wrap 22 and the end plate Steps 29a and 29b are provided in each of the connection portions (tooth bottoms) to 21. As shown in FIG. 4B, steps 39 a and 39 b are similarly provided on the tooth tip and the tooth bottom of the wrap 32 for the orbiting scroll 30. The steps 29a and 29b of the fixed scroll 20 and the steps 39a and 39b of the orbiting scroll 30 do not interfere with each other in a normal state. However, when the orbiting scroll 30 is displaced in the circumferential direction and a twist generated between the orbiting scroll 30 and the fixed scroll becomes large, for example, the step 29a of the fixed scroll 20 and the step 39b of the orbiting scroll 30 are also performed. And step 39a of the orbiting scroll 30 may come into contact with each other. In this case, the desired airtightness is impaired, so that the compression performance is lowered, or the wraps 22 and 32 may be damaged. As in this embodiment, the amount of displacement of the bearing 42 in the circumferential direction is kept small, and the displacement in the circumferential direction of the orbiting scroll 30 is restrained to avoid contact between steps in the 3D type scroll compressor 1. it can.

[Second Embodiment]
Next, a second embodiment of the present invention will be described with reference to FIGS . 5 (a) to 5 (c) .
Since the basic configuration of the scroll compressor according to the second embodiment is the same as that of the scroll compressor 1 of the first embodiment, a support structure for the bearing 42 in the boss 38 which is a difference will be described below.

In the boss 38 in the second embodiment, the inner wall 38a has a perfect circle, and the outer shape of the bearing 42 has a perfect circle. A ring-shaped elastic member 48 is fitted on the outer periphery of the bearing 42. However, the elastic member 48, the inner peripheral shape is corresponding to the outer shape of the bearing 42 is formed into a true circle, the outer periphery is formed in an oval having a major axis A _L and a minor axis As. That is, the elastic member 48, the major axis _{A L} direction thickness tθ is thicker than the minor diameter As the direction of the thickness tr. Then, the elastic member 48, minor As is along the radial direction, and, as the major axis A _L is along the circumferential direction, are fitted on the outer periphery of the bearing 42.

Here, when the diameter of the inner wall 38a and _{D 0,} the diameter _{D 0,} the major axis _{A L} and the minor axis As, has the following relationship.
Diameter D ₀ = major axis A _L > minor axis As
That is, the elastic member 48 disposed around the bearing 42 inside the boss 38 is between the inner wall 38a and the clearance corresponding to (D ₀ −As) / 2 = δr in the radial direction of the swivel plate 35. However, there is no clearance in the circumferential direction of the swivel plate 35 . Therefore, the bearing 42 (crank pin 43) including the elastic member 48 is allowed to be displaced in the radial direction by an amount corresponding to the clearance (2 × δr). On the other hand, in the circumferential direction, the bearing 42 can be displaced, but is limited to the range of the amount that the elastic member 48 can compress, and this allowable displacement is smaller than the allowable displacement in the radial direction (2 × δr).

  As described above, also in the second embodiment, as in the first embodiment, even if the orbiting scroll 30 is thermally expanded, the bearing 42 absorbs the displacement in the radial direction, but in the circumferential direction. Since the amount of displacement can be kept small, the orbiting scroll 30 can be prevented from being twisted with respect to the fixed scroll 20.

Next, if the orbiting scroll 30 is produced by casting, for example, the surface accuracy of the inner wall 38a is insufficient, and it is necessary to perform machining. At this time, in processing the oval as in the first embodiment is processed whereas it is necessary to reciprocate a tool such as a milling cutter in the long diameter D _L direction, the circularity as in the second embodiment All you need to do is move the tool in the axial direction. Therefore, the second embodiment is easier to process the boss 38 than the first embodiment.

[Third Embodiment]
Next, a third embodiment according to the present invention will be described with reference to FIG.
The basic configuration of the scroll compressor 3 according to the third embodiment is the same as that of the scroll compressor 2 of the second embodiment, and the inner wall 38a of the boss 38 is a perfect circle. Therefore, the following description will focus on the elastic member 49 that is a difference from the second embodiment.

The elastic member 49 of the third embodiment includes four arc-shaped segments 49a, 49b, 49c and 49d. The segments 49a, 49b, 49c and 49d are arranged at equal intervals between the bearing 42 and the inner wall 38a.
Each of the segments 49a, 49b, 49c, and 49d is made of an elastic body, and has the same shape and dimensions. However, the segments 49a, 49b and the segments 49c, 49d have different elastic coefficients. To do. That is, the segments 49a and 49b are made of the same material M1, the elastic coefficient of the material is E1, the segments 49c and 49d are made of the same material M2, and the elastic coefficient of the material is E2. However, the elastic modulus E 1 is also large Ri good elasticity coefficient E 2 (E1> E2).

In the third embodiment, the segments 49a and 49b having a large elastic coefficient E1 are arranged along the circumferential direction, and the segments 49c and 49d having a small elastic coefficient E2 are arranged along the radial direction. Therefore, the bearing 42 whose periphery is constrained by the elastic members 49 (segments 49a, 49b, 49c, and 49d) is easily displaced in the radial direction, and compared with this, it is difficult to displace in the circumferential direction. The allowable displacement amount δr in the radial direction is larger than the allowable displacement amount δθ in the circumferential direction.

  As described above, the scroll compressor 1 according to the third embodiment has the same effect as that of the second embodiment, and the elastic member 49 is divided into segments 49a, 49b, 49c and 49d. Therefore, it is easier to mount around the bearing 42 than the ring-shaped elastic member 48. Further, since the thickness of the segments 49a, 49b, 49c and 49d is constant, the elastic member 49 can be easily manufactured.

  The preferred embodiments of the present invention have been described above. However, unless departing from the gist of the present invention, the configurations described in the first to third embodiments are selected or changed to other configurations as appropriate. Is possible.

  For example, the present invention in which the displacement allowable amount δr is made larger than the displacement allowable amount δθ for all of the three rotation prevention mechanisms 40 arranged evenly in the circumferential direction of the orbiting scroll 30 is applied. However, at least one rotation prevention mechanism is used. The present invention may be applied to.

In the first embodiment, the permissible displacement δr is made larger than the permissible displacement δθ by making the opening shape of the inner wall 38a an ellipse. However, while the opening shape of the inner wall 38a is a perfect circle, By interposing another member such as a member in the circumferential direction of the inner wall 38a, the allowable displacement amount δr can be made larger than the allowable displacement amount δθ.
The first embodiment shows an example in which the opening shape of the inner wall 38a is an ellipse. However, if the displacement allowance δr can be made larger than the displacement allowance δθ, the shape need not be limited to an ellipse. A rectangular opening shape can also be used. The same applies to the elastic member 48 of the second embodiment.

In the second and third embodiments, the elastic members 48 and 49 are interposed between the outer ring of the bearing 42 and the inner wall 38a. However, the elastic member is provided between the inner ring of the bearing 42 and the crank pins 43 and 47. It can also be interposed.
Moreover, the elastic member 48 of 2nd Embodiment can also be divided | segmented into a some segment like 3rd Embodiment. In this case, each segment has the same thickness, but the number of segments interposed in the circumferential direction rather than the radial direction may be increased. For example, if one segment is interposed in the radial direction but two segments are interposed in the circumferential direction, the allowable displacement amount δr can be made larger than the allowable displacement amount δθ.
Furthermore, although 3rd Embodiment showed the example which divided | segmented the elastic member 49 into four segments 49a-49d, it is set as the elastic member 49 which consists of a composite material which integrally formed two types of materials from which an elastic coefficient differs. You can also.

  In addition, the scroll compressor 1 is merely an example, and the present invention can be widely applied to a scroll compressor using a pin crank type rotation prevention mechanism.

DESCRIPTION OF SYMBOLS 1 Scroll compressor 10 Housing 10a 1st housing 10b 2nd housing 11b, 11c, 11d Accommodating chamber 12 Discharge port 20 Fixed scroll 21 End plate 21a Low step part 21b High step part 21e Through-hole 22 Lap 23 Chip seal 24 Cooling fin 26 Outer peripheral wall 27 Suction port 29a, 29b Step 30 Orbiting scroll 31 End plate 31a Low step portion 31b High step portion 31c Concave groove 32 Lap 33 Chip seal 34 Cooling fin 35 Revolving plate 36 Boss 37 Bearing 38 Boss 38a Inner wall 39a, 39b Step 40 Anti-rotation mechanism 41 First element 42 Bearing 43 Crank pin (first pin)
44 Eccentric shaft 45 Second element 46 Bearing 47 Crank pin (second pin)
48, 49 Elastic members 49a, 49b, 49c, 49d Segment 50 Drive shaft 51 Connection end 53 Eccentric shaft 54 Main bearing 55 Sub bearing A _L Long diameter As Short diameter D Diameter D ₀ diameter D _{L long} diameter D _S Short diameter δr Displacement allowance δθ Allowable displacement

Claims (4)

With fixed scrolling,
A revolving orbiting motion with respect to the fixed scroll, and a revolving scroll combined to form a compression space for compressing fluid between the fixed scroll, and
A rotation prevention mechanism for the orbiting scroll,
The fixed-side wrap and the turning-side wrap are each provided with a step at the tooth tip and the root, so that the outer peripheral side is taller than the inner side,
The three rotation prevention mechanisms are arranged at equal intervals in the circumferential direction,
Each of the rotation prevention mechanisms is
A pin crank having a first pin and a second pin;
A first bearing held in a bearing box integral with the orbiting scroll and supporting the first pin;
A second bearing that is held in a second bearing housing space provided in the vicinity of the bearing box or the fixed scroll and supports the second pin,
An allowable displacement amount of the first pin in the radial direction of the orbiting scroll is δr,
When the allowable displacement amount δθ of the first pin in the circumferential direction of the orbiting scroll is
δr> δθ
Satisfied ,
The rotation prevention mechanism is
Opening of the bearing boxes, the radially has a major axis, and a scroll compressor characterized that you have a shape having a minor axis in the circumferential direction. The opening of the bearing box has an oval shape,
The scroll compressor according to claim 1 . The first bearing held in the bearing box has a perfect circle outer shape.
The scroll compressor according to claim 2 . The first pin and the second pin are integrally connected via an eccentric shaft,
The first pin, the second pin, and the eccentric shaft constitute an integral crankshaft.
The scroll compressor as described in any one of Claims 1-3 .

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