CN217873256U - Electric scroll compressor - Google Patents

Abstract

The utility model discloses an electric scroll compressor, which comprises a main shaft, a movable scroll disk, a bearing seat and a static scroll disk, wherein a crank pin type motion conversion mechanism is arranged between the main shaft and the movable scroll disk, the motion conversion mechanism comprises an eccentric pin which is arranged on the main shaft and has an eccentricity of e, the eccentric pin and the main shaft form a first crank pin, and the eccentric pin is connected with the movable scroll disk; the motion conversion mechanism also comprises an anti-rotation structure which is formed by combining a pin type and a ball type; the ball type is arranged between the movable scroll disk and the bearing seat; the pin type comprises two pin shafts with the eccentricity of e, and the two pin shafts form a second crank pin through a connecting block and are respectively and rotationally connected with fixed components on the movable scroll disk and the compressor. The beneficial effects of the utility model are that, eliminated the line contact mode of round pin axle, reduced round pin axle wearing and tearing hidden danger and operating noise, slow down the wearing and tearing between the sound whirlpool dish, do benefit to compressor life-extension. The pressure of the air inlet can not be obviously increased in the pressure increasing process of the air outlet, and the compression effect is obviously improved.

Description

Electric scroll compressor

Technical Field

The utility model relates to a scroll compressor, in particular to electronic scroll compressor.

Background

An electric scroll compressor is a compressor of an integrated structure composed of an electric motor and a scroll compressor, and has been widely used in an air conditioning system for a vehicle. The scroll compressor is a volume type machine, and its compression cavity is formed from static scroll disk with scroll ring form and moving scroll disk with identical form which are mutually staggered by 180 deg. phase angle, and the scroll ring forms of both them are involute curve. The movable scroll disk is driven by a crank shaft to do planar circular motion around the center of the fixed scroll disk, and the movable scroll disk completes the whole processes of gas suction, compression and discharge after circular motion of three planes. The plane circular motion of the movable scroll disk is obtained by converting the continuous rotary motion of the main shaft through a conversion mechanism, and the most common conversion mechanism applied at present is an eccentric pin mechanism. The mechanism comprises an eccentric pin which synchronously rotates along with a main shaft, the eccentric pin is rotationally connected to a movable scroll disk, the movable scroll disk is limited to rotate by an anti-rotation structure, so that in the continuous rotation process of the main shaft, the rotary motion of the main shaft is converted into the planar circular motion of the movable scroll disk through the eccentric pin, and the movable scroll disk forms relative rotation relative to a bearing seat for mounting the main shaft. The existing anti-rotation structure comprises a hole-pin type structure and a cross slip ring structure, wherein the hole-pin type structure comprises a hole-pin structure and a ball structure, a pin in the hole-pin structure is combined with a circular hole, and a ball in the ball structure is combined with a retainer. The cross slip ring structure has large friction coefficient, large resistance and low mechanical efficiency due to sliding friction between the sliding block and the sliding groove, so that the energy consumption is increased. Thus, the current application is more widespread with a hole-pin type structure. In the hole pin structure, although the pin and the circular hole wall are still in sliding friction connection, the pin and the circular hole wall form line contact, the mechanical efficiency is higher than that of a surface contact structure of the cross slip ring, the manufacturing is simple, the cost is low, the anti-rotation effect is good, the function is reliable, the contact stress between vortex curves of the dynamic and static vortex disks can be effectively reduced, and the service life of the vortex disks is prolonged. However, the pin still needs to bear the axial load of the movable scroll, and the pin and the movable scroll are still in surface contact, so that a part of reactive loss still exists. There is room for further improvement. In the ball structure, rolling friction is formed through the balls to bear axial load, so that the mechanical efficiency can be effectively improved, and the energy consumption is reduced. However, the ball receiving holes of the cage are spherical surfaces, and in order to ensure the reliability of the anti-rotation function, a plurality of balls and corresponding ball receiving holes are required to be densely distributed, and the cage is usually made of steel and is subjected to heat treatment such as quenching to improve hardness, enhance wear resistance, and prolong the service life. However, the retainer is a circular thin plate, so that deformation is easily generated in the heat treatment process, the precision is affected, only a few balls are in contact with the inner wall of the accommodating hole of the retainer, local abrasion of the retainer is easily generated, further, local stress of the scroll is intensified, local abrasion of the scroll is caused, the gas compression performance is affected, and the manufacturing difficulty under the conditions of ensuring reliability and prolonging the service life is increased. Therefore, through improvement, the applicant adopts two anti-rotation structures of a ball type and a hole pin type, so that the ball type anti-rotation structure only bears the axial load of the movable scroll disk, wherein the ball receiving hole of the retainer has enough space for movement of balls, the hole pin type anti-rotation structure only bears radial force, and the shaft ends of the pin columns have no friction, so that the respective advantages of the ball type anti-rotation structure and the hole pin type anti-rotation structure are exerted, the manufacturing difficulty is effectively reduced, the mechanical efficiency is improved, the energy consumption is reduced, and the service life is prolonged. The improved structure was patented by the national intellectual property office at 15/6/2021, which was granted at 26/11/2021 under the grant publication No. CN214887683U. However, the hole-pin type anti-rotation structure of the patent is composed of two pin shafts respectively fixed on the movable scroll disk and the bearing seat and a circular ring sleeved on the two pin shafts. In the compressor working process, the round pin axle forms tangent sliding friction with the ring, has the friction noise, and after long-time work, can cause round pin axle and ring wearing and tearing, has not only increased the noise and still leads to the aggravation of sound whirlpool dish joint envelope surface wearing and tearing easily, leads to under the same exhaust pressure condition, and air inlet pressure increases, has reduced the pressure differential of inlet and outlet mouth to reduce compression effect. For this reason, further improvement is required.

Disclosure of Invention

The utility model aims at providing a prevent that rotation structure still exists sliding friction's not enough to current scroll compressor, an electronic scroll compressor is provided, this compressor prevents that two round pin axle fixed connection of rotation structure are in the same place or form integratively through round pin axle and hole complex pin type, thereby form the crank pin, rotate through first bearing and the fixed component that moves the whirlpool dish of next-door neighbour on moving whirlpool dish and the compressor respectively and be connected the back, move whirlpool dish free rotation with another rotation structure common restriction of ball structure, and form the plane circular motion under the combined action of eccentric pin. The linear contact working mode of the pin shaft is eliminated, the hidden danger of pin shaft abrasion and working noise are reduced, further, the frictional abrasion between the dynamic and static vortex disks is slowed down, and the service life of the compressor is prolonged.

In order to achieve the above purpose, the present invention adopts the following technical solution.

An electric scroll compressor comprises a main shaft, a movable scroll, a bearing seat and a static scroll, wherein a crank pin type motion conversion mechanism is arranged between the main shaft and the movable scroll, the motion conversion mechanism comprises an eccentric pin which is arranged on the main shaft and has an eccentricity of e, the eccentric pin and the main shaft form a first crank pin, the eccentric pin is connected with the movable scroll through a middle hole of the movable scroll, and the motion conversion mechanism further comprises an anti-rotation structure which is formed by combining a pin type anti-rotation structure and a ball type anti-rotation structure; the ball type anti-rotation structure is arranged between the movable scroll disk and the bearing seat; the pin type anti-rotation structure comprises two pin shafts with the eccentricity of e, the two pin shafts are integrated or fixedly connected together through a connecting block to form a second crank pin, and the two pin shafts are respectively and rotationally connected with the movable scroll disk and a fixed component close to the movable scroll disk on the compressor through a first bearing.

Adopt aforementioned technical scheme the utility model discloses, two round pin axle fixed connection through preventing the rotation structure with round pin axle and hole complex pin type are in the same place or form an organic wholely to form the second crank pin, and move the fixed component that whirlpool dish was moved to the next-door neighbour through first bearing and on moving whirlpool dish and the compressor respectively and move the connection back, move whirlpool dish free rotation with another rotation structure common restriction of ball structure, and form the plane circular motion under the same eccentricity is the first crank pin combined action of e. The linear contact working mode of the pin shaft is eliminated, the hidden danger of pin shaft abrasion and working noise are reduced, further, the frictional abrasion between the dynamic and static vortex disks is slowed down, and the service life of the compressor is prolonged. Especially, two pin shafts are integrated or fixedly connected together through a connecting block, so that the second crank pin forms a rigid structure, and compared with the movable connection that the two pin shafts are contacted with each other and rotate relatively and the movable range of the second crank pin is limited by a ferrule, the airtightness of a containing cavity formed between the dynamic vortex disk and the static vortex disk is kept not to be changed obviously in the process that the pressure of an exhaust port of the compressor is gradually increased from low to high, so that the air pressure of an air inlet cannot be obviously increased, and the compression effect can be obviously improved. The fixed member on the compressor close to the movable scroll is formed by bearing seat or fixed scroll, or other member fixed on the compressor shell or the part of the compressor shell projected toward the axle center of the main shaft. In addition, the first bearing can adopt a sliding bearing and a rolling bearing, and is a compact structure, and a needle bearing is preferred. Because two round pin axles extend dorsad, mutually noninterfere in the course of the work, its diameter can be as required and installation space adjustment. When the second crank pin adopts a combined structure, a column hole matching structure is adopted to be connected with the connecting block, the pin shaft can adopt a step shaft structure, and also can adopt a straight-through shaft structure with equal diameter, and when the diameter of the matching section of the pin shaft and the bearing needs to be adjusted, the step shaft structure is suitable to be adopted.

Preferably, the ball type anti-rotation structure comprises balls, a first retainer and a second retainer, wherein the balls are positioned between the opposite surfaces of the movable scroll and the bearing seat, and are exposed from two ends of a receiving hole in the two retainers and then are in rolling connection with the movable scroll and the bearing seat; the first retainer is fixedly connected to the bearing seat; the second retainer is fixedly connected to the movable scroll. The retainer and the corresponding component form a split structure, so that the processing convenience is ensured; preferably, a detachable connection mode is adopted, so that the retainer can be conveniently replaced after being damaged, and the maintenance convenience is improved. To save cost and weight, the first and second holders may be made of nylon or plastic by injection molding.

Preferably, the movable scroll disk and the bearing seat are respectively provided with a wear-resistant gasket, and the movable scroll disk and the bearing seat are respectively in rolling connection with the balls through the wear-resistant gaskets; the receiving holes of the first retainer and the second retainer are both in a horn shape. The wear-resistant gasket is arranged to improve local wear resistance, and is replaced after local wear, so that the service life of a product is prolonged.

More preferably, the movable scroll disc and the bearing seat are both provided with annular grooves, and the wear-resistant gaskets are embedded through the annular grooves; the plane of the wear-resistant washer on the bearing seat, which is contacted with the ball, is flush with the joint surface of the bearing seat and the first retainer; and the plane of the abrasion-resistant gasket positioned on the movable scroll disk and contacted with the ball is flush with the joint surface of the movable scroll disk and the second retainer. So that the wear-resistant gasket is directly placed in the ring groove, and the assembly and maintenance efficiency is improved. And under the condition that the wear-resistant gasket is arranged in the annular groove, the whole plane is simultaneously ground, the processing convenience is improved, the whole flatness is ensured, and the size chain calculation is simplified, so that the design efficiency in the design stage is effectively improved, the product development period is shortened, the development cost is reduced, the product can be released as soon as possible, and the market first opportunity is seized.

Still more preferably, the receiving hole has a trumpet taper angle of 60 ° to 90 °. The ball bearing has spherical structure, and the horn-shaped conic surface is used to limit the motion locus of the ball bearing and replace straight hole with great diameter, so that the strength of the retainer is raised and the service life is prolonged.

Still further preferably, the first holder and the second holder are provided with integral multiple of 3 receiving holes, and are divided into three groups, adjacent groups have a set distance therebetween, and the second crank pin is located in the set distance between the adjacent groups. So that the pin shaft type anti-rotation structure can be closer to the retainer in the radial direction, the radial size is reduced, the space is saved, and the volume of the compressor is reduced.

The beneficial effects of the utility model are that, eliminated the line contact mode of round pin axle, reduced round pin axle wearing and tearing hidden danger and operating noise, and then slowed down the friction and wear between the sound whirlpool dish, can be by low rising in-process gradually to high at compressor gas vent pressure, keep the appearance chamber seal that forms between the sound whirlpool dish not take place obvious change to make air inlet pressure can obviously not rise, showing and promote the compression effect.

Drawings

Fig. 1 is a schematic perspective view of the structure of embodiment 1 of the present invention.

Fig. 2 is a schematic cross-sectional view of embodiment 1 of the present invention.

Fig. 3 is a structure schematic axonometric view of the second crank pin of the present invention.

Fig. 4 is a schematic perspective view of a bearing seat portion in embodiment 1 of the present invention.

Fig. 5 is a schematic perspective view of the orbiting scroll part in embodiment 1 of the present invention.

Fig. 6 is a partially enlarged view of fig. 2 according to the present invention.

Figure 7 is a schematic cross-sectional view of embodiment 2 of the present invention.

Fig. 8 is a schematic perspective view of a part of the structure of embodiment 2 of the present invention.

Detailed Description

The present invention will be further described with reference to the accompanying drawings, which are not intended to limit the scope of the embodiments described herein.

Embodiment 1, referring to fig. 1, 2, 3, 4, 5, and 6, an electric scroll compressor includes a main shaft 1, a movable scroll 2, a bearing seat 3, and a fixed scroll (not shown in the drawings), a crank pin type motion conversion mechanism is disposed between the main shaft 1 and the movable scroll 2, wherein the motion conversion mechanism includes an eccentric pin 1a disposed on the main shaft 1 and having an eccentricity e, the eccentric pin 1a and the main shaft 1 form a first crank pin, and the eccentric pin 1a is connected to the movable scroll 2 through a central hole of the movable scroll 2; the motion conversion mechanism further comprises an anti-rotation structure, the anti-rotation structure is formed by combining a pin type anti-rotation structure and a ball type anti-rotation structure, and the ball type anti-rotation structure is arranged between the movable scroll disk 2 and the bearing seat 3; the pin type anti-rotation structure comprises two pin shafts with the eccentricity of e, the two pin shafts are integrated through a connecting block or fixedly connected together to form a second crank pin 6, and the pin shafts are respectively in rotating connection with the movable scroll disk 2 and the bearing seat 3 through a first bearing 13 of a needle bearing. Specifically, the two pins are formed by a first pin 4 and a second pin 5, and the facing ends of the first pin 4 and the second pin 5 are connected together through a connecting block or are integrally formed through the connecting block to form a second crank pin 6, and a gap with a set distance is formed between the connecting block and the facing surfaces of the movable scroll 2 and the bearing seat 3.

The ball type anti-rotation structure comprises balls 7, a first retainer 8 and a second retainer 9, wherein the balls 7 are positioned between the opposite surfaces of the movable scroll 2 and the bearing seat 3, and are simultaneously exposed from two ends of a receiving hole in the two retainers to form rolling connection with the movable scroll 2 and the bearing seat 3; the receiving holes of the first retainer 8 and the second retainer 9 are both in a horn shape; the first retainer 8 is fixedly connected to the bearing block 3; the second retainer 9 is fixedly connected to the orbiting scroll 2. The first retainer 8 and the second retainer 9 are respectively detachably and fixedly connected with the corresponding movable scroll 2 and the corresponding bearing seat 3 by screws, the horn-shaped big ends of the receiving holes in the first retainer 8 and the second retainer 9 are oppositely arranged, and the horn-shaped taper angle of the receiving holes is 60-90 degrees. Specifically, the angle can be 60 degrees or 90 degrees, and the proved range of 70 degrees to 80 degrees is better.

In addition, wear-resistant gaskets 10 are arranged on the movable scroll 2 and the bearing seat 3, and the wear-resistant gaskets 10 are used for forming rolling connection between the movable scroll 2 and the bearing seat 3 through the wear-resistant gaskets 10 and the balls 7 respectively. Specifically, annular grooves are formed in the movable scroll 2 and the bearing seat 3, and the wear-resistant gaskets 10 are embedded in the annular grooves. The plane of the wear-resistant washer 10 on the bearing seat 3, which is contacted with the ball 7, is flush with the joint surface of the bearing seat 3 and the first retainer 8; the plane of the wear-resistant gasket 10 of the orbiting scroll 2 contacting the balls 7 is flush with the joint surface of the orbiting scroll 2 and the second retainer 9.

In this embodiment, the number of the second crank pins 6 is three, the three are uniformly arranged in the circumferential direction, the first pins 4 of the three second crank pins 6 are uniformly arranged around the axis of the second bearing 11 on the bearing seat 3 as the center of circle, the second pins 5 are uniformly arranged around the axis of the third bearing 12 arranged in the central hole of the movable scroll disk 2 as the center of circle, the eccentric pin 1a on the main shaft 1 is connected with the inner ring of the third bearing 12, and the eccentric pin 1a is further fixedly connected with the balance block 1b. The first retainer 8 and the second retainer 9 of the ball type anti-rotation structure are all arranged according to 12 ball receiving holes, every 4 ball receiving holes are in one group, a set distance is arranged between each group, the ball type anti-rotation structure is located in the space of the set distance, and a set space is vacated for the second crank pin 6 through radial adduction, so that the radial size is reduced, the structure is compact, the second retainer 9 further utilizes the space between adjacent groups to set screw mounting holes, and the space is fully utilized.

In the present embodiment, the diameters of the first pin 4 and the second pin 5 can be appropriately adjusted according to the need and the installation space. When second crank pin 6 adopted integrated configuration, first pin 4 and second pin 5 adopted the post hole tight fit structure to be connected with the connecting block, and first pin 4 and second pin 5 can adopt the step axle construction, also can adopt the through axle construction, when needing the diameter of adjustment and first bearing 13 cooperation section, should adopt the step axle construction.

In the embodiment, the ball 7 is made of a steel ball and can be purchased in the market directly; the first and second holders 8 and 9 are each formed by injection molding, and the material may be, but is not limited to, plastic and nylon.

The balls 7 of the ball type anti-rotation structure may be provided in 6, 9, or 15, etc. according to the power level and the structural size arrangement of the compressor.

The second crank pins 6 can also be uniformly distributed with 4, 5 or 6; the corresponding balls 7 are grouped by the number of the second crank pins 6 and are the number of the integral multiple of the number of the second crank pins 6.

In this embodiment, the first bearing 13 may also be a sliding bearing, or may also be a radial ball bearing instead of a needle bearing, and when a radial ball bearing is used, two or more radial ball bearings may be disposed on the same pin.

In this embodiment, a plurality of laterally protruding support lugs 2a are uniformly distributed on the circumference of the orbiting scroll 2, and bearing mounting holes for mounting the first bearing 13 are formed on the support lugs 2 a. To reduce material consumption and reduce the weight of the orbiting scroll and, in turn, the compressor.

Embodiment 2, referring to fig. 7 and 8, an electric scroll compressor includes a main shaft 1, a movable scroll 2, a bearing seat 3, and a fixed scroll 14, wherein an exhaust port 4b is formed at the bottom of the fixed scroll 14; wherein, the static scroll 14 is fixedly connected on the bearing seat 3 through a bolt or is fixed on the shell of the compressor through an end cover; a first pin 4 and a second pin 5 constituting the second crank pin 6 are rotatably connected with the orbiting scroll 2 and the fixed scroll 14 through a first bearing 13 of a needle bearing, respectively, and a gap with a set interval is provided between a connecting block connecting the first pin 4 and the second pin 5 and the facing surfaces of the orbiting scroll 2 and the fixed scroll 14.

Wherein, the outer wall of the static vortex disc 14 is provided with a gap 14a, the bottom of the gap 14a is provided with a bearing mounting hole for mounting the first bearing 13, and the gap 14a is provided with a space for accommodating the second crank pin 6 and the support lug 2a of the movable vortex disc 2.

The rest of the structure of this embodiment is the same as that of embodiment 1, and is not described herein again.

In this embodiment, the notch 14a also forms a part of the air inlet passage of the compressor, which is beneficial to the air inlet of the compressor and can reduce the pressure of the air inlet.

In this embodiment, a lubricating oil hole for lubricating the first bearing 13 may be further provided on the fixed scroll 14.

In the above embodiment, the second crank pin 6 may be provided between the orbiting scroll 2 and another fixed member formed of another member fixed to the compressor housing or a portion of the compressor housing partially protruding toward the axis of the main shaft.

In the scroll compressor of the embodiment of the present application, the applicant obtains a verification result of significantly improving the technical effect through a comparison test of two pin shafts and a circular ring in the prior art, and the intake pressures at the same exhaust pressure are significantly different except that the noise is significantly reduced by 2-4 db, which is specifically shown in the following table.

As can be seen from the table, when the discharge pressure of the compressor is 1.3 MPa, 1.4 MPa, 1.5 MPa, 1.6 MPa and 1.7MPa respectively, the inlet pressure of the prior art scroll compressor with the two pin shafts and the annular structure is 0.26 MPa, 0.28 MPa, 0.32MPa, 0.33 MPa and 0.34 MPa respectively. And the utility model discloses a compressor of 6 structures of second crank pin, it corresponds air inlet pressure and is 0.24MPa, 0.25 MPa, 0.27 MPa and 0.27 MPa respectively.

It can be seen that, the scroll compressor of the present invention has no obvious change in the process of gradually increasing the exhaust pressure, and has an intake-exhaust pressure difference of 1.43MPa under the exhaust pressure of 1.7 MPa. In the prior art, the exhaust pressure of the scroll compressor is gradually increased, the intake pressure is obviously increased, and the intake-exhaust pressure difference of 1.36MPa can be maintained at the exhaust pressure of 1.7 MPa. Obviously, the utility model discloses a scroll compressor compression effect is better.

The basic principles and the main features of the invention and the advantages of the invention have been shown and described above. It will be understood by those skilled in the art that the present invention is not limited to the above embodiments, and that the foregoing embodiments and descriptions are provided only to illustrate the principles of the present invention without departing from the spirit and scope of the present invention. The scope of the invention is defined by the appended claims and equivalents thereof.

Claims (10)

1. An electric scroll compressor comprises a main shaft (1), a movable scroll (2), a bearing seat (3) and a static scroll, wherein a crank pin type motion conversion mechanism is arranged between the main shaft (1) and the movable scroll (2), the motion conversion mechanism comprises an eccentric pin (1 a) which is arranged on the main shaft (1) and has an eccentricity of e, the eccentric pin (1 a) and the main shaft (1) form a first crank pin, the eccentric pin (1 a) is connected with the movable scroll (2) through a middle hole of the movable scroll (2), the motion conversion mechanism further comprises an anti-rotation structure, and the anti-rotation structure is formed by combining a pin type anti-rotation structure and a ball type anti-rotation structure; the ball type anti-rotation structure is arranged between the movable scroll disc (2) and the bearing seat (3); the cylindrical pin type anti-rotation structure is characterized by comprising two pin shafts with the eccentricity of e, wherein the two pin shafts are integrated or fixedly connected together through a connecting block to form a second crank pin (6) and are respectively and rotationally connected with the movable scroll disc (2) and a fixed component close to the movable scroll disc (2) on a compressor through a first bearing (13).

2. The electric scroll compressor according to claim 1, wherein the first bearing (13) is constituted by a rolling bearing.

3. The electric scroll compressor of claim 2, wherein the rolling bearing is comprised of a needle bearing.

4. An electrically driven scroll compressor according to claim 1, wherein the fixed member on the compressor immediately adjacent to the orbiting scroll (2) is constituted by a bearing housing (3) or a fixed scroll.

5. The electric scroll compressor according to any one of claims 1 to 4, wherein the ball type anti-rotation structure comprises balls (7), a first retainer (8) and a second retainer (9), the balls (7) are located between facing surfaces of the orbiting scroll (2) and the bearing housing (3) and are simultaneously exposed from both ends of receiving holes in the two retainers to form rolling connection with the orbiting scroll (2) and the bearing housing (3); the first retainer (8) is fixedly connected to the bearing seat (3); the second retainer (9) is fixedly connected to the movable scroll (2).

6. The electric scroll compressor according to claim 5, wherein the movable scroll (2) and the bearing seat (3) are provided with wear-resistant gaskets (10), and the movable scroll (2) and the bearing seat (3) are respectively in rolling connection with the balls (7) through the wear-resistant gaskets (10); the receiving holes of the first retainer (8) and the second retainer (9) are in a horn shape.

7. The electric scroll compressor according to claim 6, wherein annular grooves are formed in the orbiting scroll (2) and the bearing seat (3), the wear-resistant washers (10) are embedded through the annular grooves, and a plane of the wear-resistant washer (10) on the bearing seat (3) contacting the balls (7) is flush with a joint surface of the bearing seat (3) and the first retainer (8); the plane of the wear-resistant gasket (10) positioned on the movable scroll (2) and contacted with the ball (7) is flush with the joint surface of the movable scroll (2) and the second retainer (9).

8. The electrically driven scroll compressor of claim 6, wherein the flared cone angle of the receiving bore is between 60 ° and 90 °.

9. The electrically driven scroll compressor of claim 5, wherein the first and second cages (8, 9) are provided with an integral multiple of 3 receiving holes and are each divided into three groups with a set pitch between adjacent groups and the second crank pin (6) is located within the set pitch between adjacent groups.

10. The electric scroll compressor according to claim 5, wherein the first and second holders (8, 9) are each injection molded from nylon or plastic.

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