JP2023032662A - scroll compressor - Google Patents

Abstract

To provide a scroll compressor with further improved quietness.SOLUTION: A scroll compressor comprises: a rotational shaft rotating around an axial line by an electric motor; a revolving scroll that revolves around the axial line; a bearing part housed in the bearing housing part of the revolving scroll; and a fixed scroll. The bearing housing part is a concave part extending along an eccentric shaft radially displaced from the axial line, and an inner peripheral surface of the concave part has a tapered surface whose diameter gradually increases from the other side toward the one side in a direction of the eccentric shaft, and an annular first and second recessed surfaces recessed radially outward with respect to the tapered surface and extending in the circumferential direction.SELECTED DRAWING: Figure 3

Description

The present disclosure relates to scroll compressors.

A scroll compressor mainly includes a fixed scroll fixed to a housing and an orbiting scroll facing the fixed scroll to form a compression chamber therebetween. As the orbiting scroll orbits at a position eccentric from the axis of rotation, the volume of the compression chamber changes with time and the refrigerant can be compressed.

The orbiting scroll is attached to the rotary shaft via a bearing such as a needle bearing. Specifically, as shown in Patent Literature 1 below, a bearing portion is fitted in a concave portion serving as a bearing accommodating portion formed in one side surface of the orbiting scroll in the thickness direction. The diameter of the recess is large on the bottom side of the recess, while the diameter is constant on the opening side.

Japanese Patent No. 5730185

Here, it is known that in a bearing portion having an outer ring, such as a needle bearing, shoulder portions on both sides of the outer ring in the central axis direction have higher rigidity than other portions. Therefore, when a portion having a constant diameter like the concave portion according to Patent Document 1 comes into contact with the shoulder portion, the contact reaction force is concentrated on the shoulder portion. Due to this reaction force concentration, the bearing portion (outer ring) is deformed, and the surface contact with the inner wall surface of the recess is lost. As a result, noise may be generated from the bearing.

The present disclosure has been made to solve the above problems, and an object thereof is to provide a scroll compressor with further improved quietness.

In order to solve the above-described problems, a scroll compressor according to the present disclosure includes an electric motor, a rotating shaft driven by the electric motor to rotate about an axis extending in a horizontal direction, and rotating the rotating shaft A compression chamber is formed by an orbiting scroll that orbits about the axis, a bearing portion that is accommodated in a bearing accommodation portion formed in the orbiting scroll, and the orbiting scroll that is opposed to the orbiting scroll from one side in the axial direction. and a fixed scroll, wherein the bearing accommodating portion is a concave portion formed in a surface of the orbiting scroll facing the other side in the axial direction and extending in the axial direction, and an inner peripheral surface of the bearing accommodating portion A tapered surface that forms a conical surface centered on the axis and gradually expands in diameter from the other side in the axial direction toward the one side, and is connected to the one side in the axial direction of the tapered surface and is radially outward of the tapered surface. and an annular first retreat surface that retreats to and extends in the circumferential direction, and an annular second retreat surface that is connected to the other side of the tapered surface in the axial direction and retreats radially outward from the tapered surface and extends in the circumferential direction. and a receding surface.

According to the present disclosure, it is possible to provide a scroll compressor with further improved quietness.

1 is a cross-sectional view showing the configuration of a scroll compressor according to an embodiment of the present disclosure; FIG. FIG. 2 is an enlarged cross-sectional view of main parts of the orbiting scroll according to the embodiment of the present disclosure; FIG. 4 is an enlarged cross-sectional view of a main portion of the bearing housing portion according to the embodiment of the present disclosure, showing a state before the bearing portion is fitted; FIG. 4 is an enlarged cross-sectional view of a main portion of the bearing housing portion according to the embodiment of the present disclosure, showing a state after the bearing portion has been fitted.

(Structure of scroll compressor)
A scroll compressor 100 according to an embodiment of the present disclosure will be described below with reference to FIGS. 1 to 4. FIG. The scroll compressor 100 is used, for example, to compress refrigerant in an air conditioner for vehicles. As shown in FIG. 1, the scroll compressor 100 includes a rotating shaft 1, an electric motor 2, a compressor body 3, a housing 4, a cover 5, an upper bearing 6, a lower bearing 7, and a drive bush 8. and an orbiting scroll bearing (bearing portion 9).

(Structure of rotating shaft)
The rotary shaft 1 extends along the axis O and is rotatable around the axis O. As shown in FIG. The axis O extends horizontally. That is, this scroll compressor 100 is of a horizontal type. It should be noted that the horizontal direction here refers to a substantially horizontal direction, and manufacturing errors and design tolerances are allowed. The rotating shaft 1 has a rotating shaft body 10 , a small diameter portion 11 , a large diameter portion 12 and an eccentric shaft portion 13 . The rotating shaft main body 10 has a cylindrical shape centered on the axis O. As shown in FIG. The rotary shaft main body 10 has a uniform diameter dimension over the entire area in the direction of the axis O. As shown in FIG. A rotor 21 (described later) of the electric motor 2 is attached to the outer peripheral surface of the rotary shaft main body 10 .

A small diameter portion 11 is provided on one side (lower side) of the rotating shaft main body 10 in the direction of the axis O. As shown in FIG. The small-diameter portion 11 has a cylindrical shape centered on the axis O and has a diameter smaller than that of the rotating shaft main body 10 . The small diameter portion 11 is supported from one side (lower side) in the direction of the axis O by a lower bearing 7 attached to the housing 4 .

A large-diameter portion 12 is provided on the other side (upper side) of the rotating shaft main body 10 in the direction of the axis O. As shown in FIG. The large-diameter portion 12 has a columnar shape centered on the axis O and has a larger diameter dimension than the rotating shaft main body 10 . The large diameter portion 12 is radially supported by an upper bearing 6 fixed to the housing 4 . The upper bearing 6 has a bearing body 60 and a bearing support portion 61 . The bearing body 60 is a journal bearing. The bearing support portion 61 has a disc shape centered on the axis O and is fixed to the inner peripheral surface of the housing 4 .

An eccentric shaft portion 13 is provided further above the large diameter portion 12 (on the other side in the direction of the axis O). The eccentric shaft portion 13 protrudes from the large diameter portion 12 toward the other side in the axis O direction. The eccentric shaft portion 13 has a columnar shape centered on an eccentric shaft A extending parallel to the axis O and radially displaced from the axis O. As shown in FIG. Therefore, when the rotary shaft 1 rotates, the eccentric shaft portion 13 revolves (revolves) around the axis O. As shown in FIG.

(Motor configuration)
The electric motor 2 gives rotational driving force to the rotary shaft 1 . The electric motor 2 has a rotor 21 and a stator 22 . The rotor 21 is fixed to the rotating shaft main body 10 . The rotor 21 has a cylindrical shape centered on the axis O. As shown in FIG. Although not shown in detail, the rotor 21 has a plurality of magnets. The stator 22 covers the rotor 21 from the outer peripheral side. The stator 22 is formed by stacking a plurality of steel plates in the direction of the axis O, and further by winding a copper wire (forming a coil). By energizing the stator 22 , an electromagnetic force is generated between the stator 22 and the rotor 21 , and a rotational force around the axis O is applied to the rotor 21 . As a result, the rotary shaft 1 rotates around the axis O. As shown in FIG.

(Compressor body configuration)
The compressor main body 3 is driven by the rotation of the rotating shaft 1 by the electric motor 2 . The compressor main body 3 has a fixed scroll 31, an orbiting scroll 32, and an anti-rotation mechanism (not shown). The fixed scroll 31 has a disk-shaped first end plate 31a centered on the axis O, and a first spiral plate 31b provided on one side (lower side) of the first end plate 31a in the direction of the axis O. are doing. The first spiral plate 31b extends spirally around the axis O. As shown in FIG. The fixed scroll 31 is fixed to the housing 4 .

The orbiting scroll 32 has a disk-shaped second end plate 32a, a second spiral plate 32b provided on the other side (upper side) of the second end plate 32a in the direction of the axis O, and a boss portion 32c. there is The second spiral plate 32b extends spirally around the axis O. As shown in FIG. The dimension of the second spiral plate 32b in the direction of the axis O is the same as the dimension of the first spiral plate 31b in the direction of the axis O described above. By engaging the first spiral plate 31b and the second spiral plate 32b in the direction of the axis O in this manner, a compression chamber is formed between them.

The boss portion 32c is a cylindrical portion that protrudes from the second end plate 32a toward one side (lower side) in the direction of the axis O. As shown in FIG. The boss portion 32 c is attached to the eccentric shaft portion 13 of the rotating shaft 1 via the drive bush 8 and the bearing portion 9 . As the eccentric shaft portion 13 turns around the axis O, a turning force is transmitted to the orbiting scroll 32 through the drive bush 8 and the bearing portion 9 . As a result, the orbiting scroll 32 orbits around the axis O. As shown in FIG. Rotation (rotation) of the orbiting scroll 32 itself is regulated by a rotation prevention mechanism (not shown).

As the orbiting scroll 32 orbits, the volume of the compression chamber changes with time, and the refrigerant is compressed while being sent from the radially outer side to the inner side in the compression chamber, increasing the pressure. The high pressure refrigerant is guided into the housing 4 through the opening H formed in the first end plate 31 a of the fixed scroll 31 .

As shown in FIG. 1, the housing 4 includes a first housing 4a that houses the electric motor 2 and the compressor main body 3, and a second housing that covers the fixed scroll 31 by being provided on one side of the first housing 4a in the direction of the axis O. 4b, and a cover 5 that is provided integrally with the first housing 4a and accommodates electrical components.

(Structure of bearing housing)
Next, the configuration around the orbiting scroll bearing (bearing portion 9) will be described with reference to FIGS. 2 to 4. FIG. As shown in FIG. 2, the bearing portion 9 is fitted in a bearing accommodating portion 32d formed on the inner peripheral side of the boss portion 32c. That is, the drive bush 8 is rotatable around the eccentric shaft A inside the bearing accommodating portion 32d via the bearing portion 9. As shown in FIG.

As shown in FIG. 3, before the bearing portion 9 is fitted, the inner peripheral surface of the bearing accommodating portion 32d includes a tapered surface 41, a first receding surface 42, an arc surface 43, a bottom surface 44, and a second A second receding surface 45, a stepped surface 46 and a chamfered portion 47 are formed.

The tapered surface 41 forms a conical surface by gradually increasing in diameter from the other side toward the one side in the direction of the eccentric axis A (that is, from the inlet side of the bearing accommodating portion 32d toward the bottom surface 44 side). An annular first receding surface 42 is connected to one side of the tapered surface 41 in the eccentric axis A direction. The first receding surface 42 extends so as to recede (separately) radially outward with respect to the eccentric axis A as it goes from the other side in the eccentric axis A direction to the one side.

A circular arc surface 43 is connected to one side of the first retreat surface 42 in the eccentric axis A direction. The arc surface 43 connects between the bottom surface 44 of the bearing accommodating portion 32d and the first retreat surface 42 in an arc shape.

An annular second receding surface 45 is connected to the other side of the tapered surface 41 in the eccentric axis A direction. The second receding surface 45 extends so as to recede (separately) radially outward from the eccentric axis A as it goes from one side to the other side in the eccentric axis A direction. A step surface 46 is connected to the other side of the second retreat surface 45 in the eccentric axis A direction. The stepped surface 46 has a cylindrical shape extending in the eccentric axis A direction. A chamfered portion 47 is connected to the other side of the step surface 46 in the eccentric axis A direction. As with the second receding surface 45 , the chamfered portion 47 extends so as to recede (separately) radially outward from the eccentric axis A as it goes from one side to the other side in the eccentric axis A direction.

Here, as shown in FIG. 3, the angle formed by the tapered surface 41 and the first receding surface 42 is assumed to be θ1. The angle formed by the tapered surface 41 and the second receding surface 45 is θ2. At this time, the relationship θ1>θ2 is established.

Next, a state in which the bearing portion 9 is fitted into the bearing accommodating portion 32d will be described with reference to FIG. The bearing portion 9 is, for example, a shell-type needle bearing. As shown in the figure, the bearing portion 9 includes a cylindrical outer ring 91 centered on the eccentric axis A, a pair of seals 92 sealing the outer ring 91 from both sides in the direction of the eccentric axis A, and an inner ring of the outer ring 91. It has a plurality of rollers 93 circumferentially arranged along the circumferential surface and an inner ring (not shown).

When the bearing portion 9 is fitted into the bearing accommodating portion 32d, the bearing accommodating portion 32d is elastically deformed. As a result, the outer peripheral surface 91a of the outer ring 91 and the tapered surface 41 come into surface contact. Further, the axial end surface 91b of the outer ring 91 facing the direction of the eccentric axis A, the seal 92, and the bottom surface 44 come into surface contact. On the other hand, the first receding surface 42 and the arcuate surface 43 do not contact the outer peripheral surface 91a, but face each other with a gap in the radial direction. Similarly, the second receding surface 45, the stepped surface 46, and the chamfered portion 47 do not contact the outer peripheral surface 91a, but face each other with a gap in the radial direction.

Further, as shown in FIG. 4, the length in the direction of the eccentric axis A of the portion of the outer peripheral surface 91a of the outer ring 91 facing the first retreating surface 42 is a1, and the eccentric axis of the portion facing the second retreating surface 45 is a1. When the length in the A direction is a2 and the thickness of the outer ring 91 in the radial direction is t, the relationships of the following expressions (1) and (2) are satisfied.
0≦a1≦t (1)
0≦a2≦t (2)

(Effect)
Next, the operation of scroll compressor 100 will be described. In order to operate the scroll compressor 100, electric power is supplied to the electric motor 2 first. As a result, the rotary shaft 1 rotates around the axis O. As shown in FIG. The orbiting scroll 32 orbits around the axis O as the rotating shaft 1 rotates. With this swirl, the volume of the compression chamber changes with time, and the refrigerant is gradually compressed. The compressed refrigerant is introduced outside and used for various purposes.

Here, it is known that, like the needle bearing described above, in the bearing portion 9 having the outer ring 91, the rigidity of the shoulder portions on both sides of the outer ring 91 in the central axis direction is higher than that of other portions. A shoulder refers to a corner formed by the seal 92 and the outer ring 91 . Therefore, for example, if the entire tapered surface 41 abuts against the shoulder without forming the first receding surface 42 and the second receding surface 45, the contact reaction force concentrates on the shoulder. Due to the concentration of this reaction force, the bearing portion 9 (outer ring 91) is deformed, and the inner wall surface of the bearing accommodating portion 32d is no longer in surface contact. As a result, the contact position between the rollers 93 and the outer ring 91 is biased, and there is a risk that noise will be generated from the bearing portion 9 . Therefore, in the present embodiment, the tapered surface 41, the first receding surface 42, and the second receding surface 45 are formed in the bearing accommodating portion 32d.

According to the above configuration, since the inner peripheral surface of the bearing housing portion 32d has the tapered surface 41, even if a force is applied to the bearing portion 9 in a direction in which the bearing portion 9 falls off from the bearing housing portion 32d, the tapered surface The force can be resisted by hooking 41 . Thereby, the possibility that the bearing portion 9 will fall off can be reduced.

Furthermore, since the first receding surface 42 and the second receding surface 45 are formed, the shoulder portion of the bearing portion 9 having high rigidity does not come into contact with the inner peripheral surface of the bearing housing portion 32d. In other words, the pressure due to the elastic deformation of the tapered surface 41 is not transmitted to the shoulder, but is borne by areas other than the shoulder. Therefore, the tapered surface 41 can be appropriately brought into surface contact with the outer peripheral surface (outer ring 91 ) of the bearing portion 9 . This makes it possible to more stably hold the bearing portion 9 inside the bearing accommodating portion 32d. As a result, uneven contact between the outer ring 91 and the rollers 93 is suppressed, and noise generated from the bearing portion 9 can be reduced.

Further, according to the above configuration, the first retreating surface 42 and the second retreating surface 45 face the outer ring 91 with a gap in the radial direction. That is, the shoulder portion of the outer ring 91 having high rigidity does not contact the inner peripheral surface of the bearing accommodating portion 32d. Therefore, only the tapered surface 41 can be appropriately brought into surface contact with the outer peripheral surface 91 a of the outer ring 91 without deforming the outer ring 91 .

Further, according to the above configuration, the length in the direction of the eccentric axis A of the portion of the outer peripheral surface 91a of the outer ring 91 that faces the first retreat surface 42 is a1, and the length of the portion that faces the second retreat surface 45 in the direction of the eccentric axis A is a1. When the length of the outer ring 91 in the radial direction is a2 and the thickness of the outer ring 91 in the radial direction is t, the relationships of the above expressions (1) and (2) are satisfied. According to this configuration, the lengths of the portion facing the first retreat surface 42 and the portion facing the second retreat surface 45 in the outer peripheral surface 91 a of the outer ring 91 can be sufficiently secured. As a result, the shoulder portion of the outer ring 91 having high rigidity does not come into contact with the inner peripheral surface of the bearing accommodating portion 32d. Therefore, only the tapered surface 41 can be appropriately brought into surface contact with the outer peripheral surface 91a of the outer ring 91 without deforming the outer ring.

In addition, according to the above configuration, the angle θ1 formed between the first retreat surface 42 (that is, the bottom surface 44 side of the bearing housing portion 32d) and the tapered surface 41 is the second retreat surface 45 (that is, that of the bearing housing portion 32d). opening side) and the tapered surface 41 is larger than the angle θ2. As a result, even if a force is applied to the bearing portion 9 in a direction in which the bearing portion 9 falls out of the bearing housing portion 32d, the first retreating surface 42 is caught by the bearing portion 9 to resist the force. can. As a result, the bearing portion 9 can be held more stably without falling out of the bearing housing portion 32d.

The embodiments of the present disclosure have been described above. Various changes and modifications can be made to the above configuration without departing from the gist of the present disclosure. For example, in the above-described embodiment, an example in which a needle bearing is used as the bearing portion 9 has been described. However, the specific aspect of the bearing portion 9 is not limited to this, and it is also possible to use other types of bearings.

<Appendix>
The scroll compressor 100 described in each embodiment is understood as follows, for example.

(1) A scroll compressor 100 according to a first aspect includes an electric motor 2, a rotating shaft 1 that is driven by the electric motor 2 to rotate around an axis O extending in a horizontal direction, and rotation of the rotating shaft 1. orbiting scroll 32 that orbits around the axis O along with the movement of the orbiting scroll 32; bearing portions 9 accommodated in bearing accommodating portions 32d formed in the orbiting scroll 32; and a fixed scroll 31 that forms a compression chamber by facing from the side, and the bearing accommodating portion 32d is formed on a surface of the orbiting scroll 32 facing the other side in the direction of the axis O, and extends radially from the axis O. The inner peripheral surface of the bearing accommodating portion 32d forms a conical surface centered on the eccentric axis A, and extends from the other side to the one side in the direction of the eccentric axis A. A tapered surface 41 that gradually expands in diameter according to the following, and an annular first retreat surface 42 that is connected to one side of the tapered surface 41 in the direction of the eccentric axis A, retreats radially outward from the tapered surface 41, and spreads in the circumferential direction. and an annular second retreat surface 45 connected to the other side of the tapered surface 41 in the direction of the eccentric axis A, retreating radially outward from the tapered surface 41 and expanding in the circumferential direction.

According to the above configuration, since the inner peripheral surface of the bearing housing portion 32d has the tapered surface 41, even if a force is applied to the bearing portion 9 in a direction in which the bearing portion 9 falls off from the bearing housing portion 32d, the tapered surface The force can be resisted by hooking 41 . Furthermore, since the first receding surface 42 and the second receding surface 45 are formed, the shoulder portion of the bearing portion 9 having high rigidity does not come into contact with the inner peripheral surface of the bearing housing portion 32d. Therefore, the tapered surface 41 can be appropriately brought into surface contact with the outer peripheral surface of the bearing portion 9 . This makes it possible to more stably hold the bearing portion 9 inside the bearing accommodating portion 32d.

(2) In the scroll compressor 100 according to the second aspect, the bearing portion 9 has a cylindrical outer ring 91 centered on the eccentric axis A, the first retreat surface 42 and the second retreat surface 42 . The surface 45 faces the edges of the outer ring 91 on both sides in the eccentric axis A direction with a gap in the radial direction.

According to the above configuration, the first receding surface 42 and the second receding surface 45 face the outer ring 91 with a gap in the radial direction. That is, the shoulder portion of the outer ring 91 having high rigidity does not contact the inner peripheral surface of the bearing accommodating portion 32d. Therefore, only the tapered surface 41 can be appropriately brought into surface contact with the outer peripheral surface 91 a of the outer ring 91 without deforming the outer ring 91 .

(3) In the scroll compressor 100 according to the third aspect, the length in the direction of the eccentric axis A of the portion of the outer peripheral surface 91a of the outer ring 91 facing the first retreat surface 42 is a1, and the second retreat When the length of the portion facing the surface 45 in the direction of the eccentric axis A is a2, and the thickness of the outer ring 91 in the radial direction is t, the following equations (1) and (2) are satisfied. .
0≦a1≦t (1)
0≦a2≦t (2)

According to the above configuration, the lengths of the portion facing the first retreat surface 42 and the portion facing the second retreat surface 45 in the outer peripheral surface 91a of the outer ring 91 can be sufficiently secured. As a result, the shoulder portion of the outer ring 91 having high rigidity does not come into contact with the inner peripheral surface of the bearing accommodating portion 32d. Therefore, only the tapered surface 41 can be appropriately brought into surface contact with the outer peripheral surface 91 a of the outer ring 91 without deforming the outer ring 91 .

(4) In the scroll compressor 100 according to the fourth aspect, in a cross-sectional view including the eccentric axis A, the angle formed by the first receding surface 42 and the tapered surface 41 is θ1, and the second receding surface 45 and the tapered surface 41, the relationship θ1>θ2 is satisfied.

According to the above configuration, the angle θ1 formed by the first retreat surface 42 (that is, the bottom surface side of the bearing housing portion 32d) and the tapered surface 41 is the second retreat surface 45 (that is, the opening side of the bearing housing portion 32d). and the tapered surface 41 are larger than the angle θ2. As a result, even if a force is applied to the bearing portion 9 in a direction in which the bearing portion 9 falls out of the bearing housing portion 32d, the first retreating surface 42 is caught by the bearing portion 9 to resist the force. can. As a result, the bearing portion 9 can be held more stably without falling out of the bearing housing portion 32d.

100 scroll compressor 1 rotating shaft 2 electric motor 3 compressor main body 4 housing 4a first housing 4b second housing 5 cover 6 upper bearing 7 lower bearing 8 drive bush 9 bearing portion (orbiting scroll bearing)
10 Rotary shaft main body 11 Small diameter portion 12 Large diameter portion 13 Eccentric shaft portion 21 Rotor 22 Stator 31 Fixed scroll 31a First end plate 31b First spiral plate 31s Main surface 32 Orbiting scroll 32a Second end plate 32b Second spiral plate 32c Boss portion 32d Bearing accommodating portion 41 Tapered surface 42 First retreat surface 43 Circular arc surface 44 Bottom surface 45 Second retreat surface 46 Stepped surface 47 Chamfered portion 60 Bearing main body 61 Bearing support portion 91 Outer ring 91a Outer peripheral surface 92 Seal 93 Roller A Eccentricity Axis H Opening O Axis

Claims (4)

an electric motor;
a rotary shaft driven by the electric motor to rotate around a horizontally extending axis;
an orbiting scroll that orbits around the axis as the rotating shaft rotates;
a bearing portion housed in a bearing housing portion formed in the orbiting scroll;
a fixed scroll that forms a compression chamber by facing the orbiting scroll from one side in the axial direction;
with
The bearing accommodating portion is a recess formed on a surface of the orbiting scroll facing the other side in the axial direction and extending along an eccentric shaft radially displaced from the axis,
The inner peripheral surface of the bearing accommodating portion is
a tapered surface that forms a conical surface centered on the eccentric shaft and that gradually expands in diameter from the other side toward the one side in the direction of the eccentric shaft;
an annular first recessed surface connected to one side of the tapered surface in the eccentric axial direction, recessed radially outward from the tapered surface, and expanding in the circumferential direction;
an annular second recessed surface connected to the other side of the tapered surface in the eccentric axis direction, recessed radially outward from the tapered surface, and expanding in the circumferential direction;
scroll compressor. The bearing portion has a cylindrical outer ring centered on the eccentric shaft,
The scroll compressor according to claim 1, wherein the first retreating surface and the second retreating surface are opposed to the edges of the outer ring on both sides in the eccentric axial direction with a gap in the radial direction. Let a1 be the length in the eccentric axis direction of the portion of the outer peripheral surface of the outer ring that faces the first retreat surface, and let a2 be the length in the eccentric axis direction of the portion that faces the second retreat surface, and the outer ring 3. The scroll compressor according to claim 2, wherein the relationship of the following formulas (1) and (2) is satisfied, where t is the wall thickness in the radial direction of the scroll compressor.
0≦a1≦t (1)
0≦a2≦t (2) In a cross-sectional view including the eccentric axis, when the angle formed by the first receding surface and the tapered surface is θ1, and the angle formed by the second receding surface and the tapered surface is θ2, θ1>θ2. The scroll compressor according to any one of claims 1 to 3, satisfying:

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