JPH10288171A - Scroll compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To keep a sleeve in parallel to an oscillating bearing, prevent lowering of bearing load capacity and prevent damage of the oscillating bearing, even if an oscillating shaft is bent or is inclined, by providing a beltlike projected part to be a projection in the axial direction and the vertical direction over the whole periphery of the inner peripheral surface of the sleeve. SOLUTION: A beltlike projected part 13 corresponds to almost the center part of an oscillating bearing 6 and is provided on the outer periphery of an oscillating shaft 12. A sleeve 14 is provided between the oscillating bearing 6 and the oscillating shaft 12. An engagement member 15 is inserted into a small hole 12e provided on the oscillating shaft 12, is fitted into a notched part 14e provided on the inner peripheral surface of the sleeve 14 with a gap and connects the sleeve 14 and the oscillating shaft 12 in the revolving directions. The sleeve 14 is capable of moving by following the inclination directions and inclination amount of the oscillating shaft 12 and the oscillating bearing 6 by making the beltlike projected part a supporting point and the sleeve 14 always revolves in a state that the sleeve 14 remains parallel to the oscillating bearing 6. Thus, abrasion and baking of the oscillating bearing 6 are prevented without lowering bearing load capacity of the oscillating bearing 6 and reliability is improved.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a scroll compressor, and more particularly, to a scroll compressor used for refrigeration and air conditioning equipment.

[0002]

2. Description of the Related Art For example, a conventional scroll compressor disclosed in Japanese Unexamined Patent Publication No. Hei 6-137284 was constructed as shown in FIG. In the figure, reference numeral 8 denotes a closed container, 9 denotes a rotor of a motor housed inside the closed container, 10 denotes a crankshaft fixed to the rotor, 5 denotes a fixed scroll disposed inside the closed container, and 1 denotes the fixed scroll. An orbiting scroll which compresses a fluid in cooperation with a fixed scroll;
0a is an eccentric hole provided at one end of the crankshaft, 6 is a swing bearing provided in the eccentric hole, 3 is a first frame, 1
1 is a main bearing provided on the first frame and rotatably supporting the crank, 4 is a second frame, and 7 is a sub-bearing provided on the second frame and rotatably supporting the crankshaft. Both the main bearing and the sub bearing are fitted to the crankshaft with a small clearance.

Next, the operation will be described. During compressor operation,
The rotational force generated by the electric motor is transmitted to the crankshaft 10, and the oscillating bearing 6 and the oscillating shaft 12 of the eccentric hole 10a are formed.
Is transmitted to the swinging scroll 1 via. Swing scroll
The orbit 1 performs a revolving motion in a circular orbit by an Oldham ring (not shown) which is a well-known anti-rotation mechanism, and the fluid is compressed according to a change in volume of a compression chamber formed between the fixed scroll 5 and the fixed scroll 5. Done. At this time, the compression load Fg of the refrigerant acting on the swing scroll 1 and the centrifugal force Fc of the swing scroll 1 act on the swing shaft 12, and the crankshaft 10 passes through the swing bearing 6. Is transmitted.

[0004]

Since the conventional scroll compressor is constructed as described above, the compression load Fg of the refrigerant and the centrifugal force Fc of the oscillating scroll act on the oscillating shaft. For this reason, a bending deformation occurs in the swing shaft. If the oscillating shaft is deformed, tilting occurs between the oscillating bearing and the oscillating shaft, causing a contact of the oscillating shaft, thereby reducing the load capacity of the oscillating bearing, causing abnormal wear and burning of the bearing. There is a problem that sticking occurs. FIG. 15 shows the state of the swing shaft that has caused deflection. In addition, the crankshaft is supported by the main bearing and the sub-bearing with a small gap, so the crankshaft is inclined due to the small gap, and the crankshaft is provided between the swing bearing and the swing shaft provided at the end of the crankshaft. Is inclined. As a result, the load capacity of the oscillating bearing decreases,
There has been a problem that abnormal wear and seizure of the bearing occur. FIG. 16 shows the state of the swing shaft that has caused the inclination.

SUMMARY OF THE INVENTION An object of the present invention is to solve such a conventional problem and to prevent the occurrence of damage such as abrasion and seizure of a bearing portion due to a contact of a swinging shaft and the like. It is an object of the present invention to obtain a highly reliable scroll compressor with high reliability without loosening or breakage of related members and a compact compressor with high productivity. Another object of the present invention is to provide a scroll compressor free from vibration and noise caused by axial movement of the sleeve.

[0006]

According to a first aspect of the present invention, there is provided a scroll compressor comprising a closed container, a fixed scroll having a spiral wrap, and a spiral wrap.
An oscillating scroll for compressing a fluid in combination with the spiral wrap of the fixed scroll, an oscillating shaft provided on the side opposite to the oscillating wrap of the oscillating scroll, and a crankshaft rotated by an electric motor A frame having a bearing for rotatably supporting the crankshaft, an eccentric hole provided at one end of the crankshaft, and a swing bearing formed on the inner peripheral surface of the eccentric hole. In the scroll compressor, the swing shaft is fitted to the swing bearing via the sleeve, and the sleeve is connected by an engagement member so as to rotate integrally with the swing shaft. , Which is rotatably fitted to the oscillating shaft, and corresponds to the axial central portion of the oscillating bearing, and corresponds to the outer peripheral surface of the oscillating shaft, or the axial central portion of the oscillating bearing. A belt-like shape which is convex in the axial direction and the vertical direction all around the inner peripheral surface of the sleeve. It is provided with a convex portion.

A scroll compressor according to a second aspect of the present invention is the scroll compressor according to the first aspect, wherein an oil reservoir for lubricating oil is provided at a lower portion of the closed vessel, an oil pump is provided at a lower portion of the crankshaft, and provided inside the crankshaft. An oil passage communicating the eccentric hole and the oil pump, and an oil groove provided in the oscillating bearing, and a substantially disk-shaped engaging member having at least one projection is fixed to the lower end of the oscillating shaft. A notch having a finite depth is provided at the lower end on the inner peripheral side of the sleeve, and the sleeve and the swing shaft are connected in the rotational direction with the protrusion and the notch;
The notch bottom of the sleeve is seated on the projection of the engaging member.

The scroll compressor according to a third aspect of the present invention is the scroll compressor according to the second aspect, wherein a lower end of the swing shaft is provided with a orbital small diameter portion which is smaller than the outer diameter of the circumferential portion of the engaging member. Then, a first concave portion is formed, a convex portion is provided on the inner peripheral portion of the sleeve, and the first concave portion is fitted with a predetermined axial gap.

In the scroll compressor according to a fourth aspect of the present invention, in the third aspect, the dimensional relationship between the axial length L1 of the sleeve and the swing bearing length L2 is set such that L1> L2. Further, when the sleeve moves in the axial direction within the axial gap formed by the sleeve convex portion and the first concave portion, the end of the sleeve does not overlap with the sliding surface of the swing bearing.

A scroll compressor according to a fifth aspect of the present invention is the scroll compressor according to the third or fourth aspect, wherein a fastening member for fastening the engaging member to the swing shaft and a fastening portion of the engaging member to the swing shaft. A second concave portion, and the small-diameter portion around the end of the pivot shaft and the second concave portion are fitted.

A scroll compressor according to a sixth aspect of the present invention is the scroll compressor according to the fifth aspect, wherein at least one flat portion is provided in the orbiting small-diameter portion at the end of the swing shaft, and the second recess of the engagement member is provided in the second recess. A flat portion corresponding to the flat portion of the orbital small diameter portion is provided.

[0012]

Embodiments of the present invention will be described below with reference to the drawings. However, in each embodiment, portions that are the same as or correspond to those of the related art are denoted by the same reference numerals, and description thereof is omitted.

Embodiment 1 FIG. FIG. 1 is an enlarged view of a main part showing the first embodiment, and FIG. 2 is a perspective view of a sleeve 14. The other structure of the compressor is the same as that shown in FIG. In the figure, reference numeral 13 denotes a substantially central portion of the oscillating bearing 6, and a band-shaped convex portion provided on the outer periphery of the oscillating shaft 12, and a substantially cylindrical member 14 provided between the oscillating bearing 6 and the oscillating shaft 12 A sleeve 15 is an engagement member. Engaging member 1
Numeral 5 is inserted into a small hole 12e provided on the swing shaft 12, is fitted with a gap into a cutout portion 14e provided on the inner peripheral surface of the sleeve 14, and connects the sleeve 14 and the swing shaft 12 in the rotational direction. ing.

Next, the operation will be described with reference to FIG. During the operation of the compressor, a centrifugal force and a gas compression load act on the swing shaft 12, and the magnitude thereof varies depending on the compressor operating conditions, so that the bending direction of the swing shaft 12 also varies. The inclination occurs between the oscillating bearing 6 and the oscillating shaft 12, and the inclination between the oscillating bearing 6 and the oscillating shaft 12 due to the minute gap between the main bearing 11 and the sub-bearing 7 shown in FIG. However, in this embodiment, the sleeve 14 can move following the inclination direction and the amount of inclination of the oscillating shaft 12 and the oscillating bearing 6 with the belt-shaped convex portion as a fulcrum. , The relief # 14 always rotates in a state parallel to the swing bearing 11.

As a result, it is possible to obtain a highly reliable bearing structure in which the bearing load capacity of the oscillating bearing is not reduced and the oscillating bearing is free from abrasion, seizure and the like.

FIG. 4 is another example showing the first embodiment.
Reference numeral 12 denotes a swing shaft, reference numeral 14 denotes a sleeve, and reference numeral 14f denotes a belt-shaped convex portion corresponding to a substantially central portion of the swing bearing 6 and provided on an inner peripheral surface of the sleeve 14. In FIG. 1, a band-shaped protrusion is provided on the swing shaft 12, but the same effect can be obtained by providing a band-shaped protrusion on the inner peripheral surface of the sleeve as shown in FIG.

FIG. 5 shows still another example of the first embodiment. Reference numeral 12 denotes a swing shaft, 14 denotes a sleeve, and 13 denotes a belt-shaped convex portion. In the example shown in FIG. 5, the belt-shaped convex portion is formed by a barrel-shaped curved surface. The sleeve 14 can move by following the inclination direction and the inclination amount of the swing shaft 12 and the swing bearing with the barrel-shaped curved surface portion 13 as a fulcrum, regardless of the operating conditions of the compressor.
The sleeve 14 always rotates in a state parallel to the swing bearing 11.

As a result, it is possible to obtain a highly reliable bearing structure free from the possibility of wear and seizure of the oscillating bearing without reducing the bearing load capacity of the oscillating bearing.
Since the belt-like convex portion 13 is formed into a barrel-shaped curved surface, there is an effect that abnormal contact wear does not occur at a contact portion between the belt-like convex portion and the inner peripheral portion of the sleeve 14.

Embodiment 2 6, 7, and 8 show the second embodiment. The arrows in the figure indicate the flow of the lubricating oil. In the figure, 16 is an oil pump, 17 is an oil reservoir, 1
8 is an oil passage provided in the crankshaft 10 and 19 is a swing bearing 6
An oil groove provided in the inner peripheral surface in the axial direction, 15 is a disk-shaped engaging member provided with a projection 15a in a radial direction, and 14a is a sleeve 1.
4 Notches of finite depth provided at the lower part of the inner circumference. The sleeve 14 is seated on the projection 15a of the engaging member 15 so that the sleeve 14 is prevented from moving downward in the axial direction.
Is fixed to the bottom of the oscillating shaft 12 by a connecting means such as a screw or welding, and a space is formed in the bottom of the eccentric hole by the lower surface of the sleeve 14, the lower surface of the engaging member 15, and the bottom of the eccentric hole.

Next, the operation will be described. Sleeve 1
4 is restricted from moving downward in the axial direction by a projection 15a and a notch 14a having a finite depth, the engagement member 15 is fixed to the bottom of the swing shaft 12, and a space is formed at the bottom of the eccentric hole. As shown by the arrows in FIGS. 6 and 7,
The oil flows into the oil groove 19 through the space between the oil passage 18 and the bottom of the eccentric hole to lubricate the swing bearing 6. The sleeve 14 and the swing shaft 12 are connected in the rotational direction by a projection 15a and a notch 14a having a finite depth.

As a result, in the scroll compressor having the structure in which the swing shaft is prevented from hitting one side (the structure shown in the first embodiment), a space can be secured between the lower portion of the sleeve 14 and the bottom of the eccentric hole. Since the oil supply path to the oscillating bearing 6 can be ensured, the supply of the lubricating oil to the oscillating bearing 6 is ensured. A more reliable bearing structure without the risk of wear, seizure, etc. of the bearing can be obtained. FIG.
Although the example where a is one is shown, a plurality of protrusions 15a may be provided. FIG. 6 shows an example in which a centrifugal pump is used as the oil pump 16, but a positive displacement oil pump may be used.

Embodiment 3 FIG. FIG. 9 shows the third embodiment. Other structures of the entire compressor are the same as those shown in FIG. In the figure, reference numeral 12a denotes a small-diameter portion provided at the lower end of the swing shaft 12, and 12b denotes a small-diameter portion 12a and the engaging member 1.
The first concave portion 14b formed by the outer peripheral portion 5 is a convex portion provided on the inner peripheral portion below the sleeve 14. The point that the engaging member 15 is fixed to the swing shaft 12 by means of screws, welding, or the like, and the relationship between the notch 14a of the sleeve 14 and the projection 15a of the tilting member 15 is the same as that of the second embodiment. The same is true.

Next, the operation will be described. The movement of the sleeve protrusion 14b in the axial direction between the swing shaft 12 and the engagement member 15 in the first recess 12b is regulated,
The sleeve 14 is restricted from moving in the axial direction. as a result,
The occurrence of abnormal vibration and noise caused by the sleeve 14 moving in the axial direction during operation and startup is reduced.

Embodiment 4 Next, a fourth embodiment will be described with reference to FIG. In the drawing, L1 is the axial length of the sleeve 14, L2 is the length of the swing bearing 6, and L3 is the axial gap formed by the convex portion 14b of the sleeve inner peripheral portion and the first concave portion 12b. . The dimensional relationship among the axial length L1 of the sleeve 14, the length L2 of the swing bearing 6 and the axial gap L3 of the sleeve is set so that L1> L2, and the sleeve 14 is made of the first material. The upper and lower ends of the sleeve 14 do not overlap with the sliding surface of the swing bearing when the sleeve 14 moves in the axial direction within the axial gap L3 formed by the concave portion 12b. The swing bearing 6 is a so-called bearing alloy made of a soft metal such as lead, tin, copper, and aluminum. The sleeve 14 is made of a material harder than the swing bearing, such as a sintered material or steel.

Next, the operation will be described. Since the dimensional relationships of the parts are set as described above, the upper and lower ends of the sleeve 14 may overlap with the swing bearing 6 when the sleeve 14 moves in the axial direction within the range of the axial gap. Abnormal wear of the swing bearing 6 can be prevented, and the reliability of the swing bearing 6 is further improved. FIG. 10 is a view showing a case where the lower end portion of the sleeve 14 and the swing bearing 6 overlap each other, not according to the present embodiment. When the lower end of the sleeve 14 and the swing bearing 6 overlap as shown in FIG.
There is a problem that the rocking bearing 6 made of a soft metal is worn by the axial movement of the sleeve 14 made of a hard metal.

Embodiment 5 11 and 12 show a fifth embodiment. 20 is the engaging member 15 and the swing shaft 12
Is a second concave portion provided in the engaging member 15, and the orbiting small-diameter portion 12a is a second concave portion 15c.
Is fitted. The other structures of the compressor are the same as those shown in FIG. 6 and the like.
And so on.

Next, a method of assembling the main part of the compressor according to the present embodiment will be described. After fitting the sleeve 14 to the swing shaft 12, the engaging member 15 is fastened to the swing shaft 12 by the fastening member 20. At this time, the second recess 15 provided in the engagement member 15
c is fitted to the orbiting small diameter portion 12a, and the engaging member 15 and the swing shaft 12
Is performed. Since the swing shaft 12, the sleeve 14, and the engaging member 15 are assembled as described above, the swing shaft 12 and the engaging member 15 can be accurately positioned when the swing shaft 12, the sleeve 14, and the engaging member 15 are assembled. A compressor is obtained.

Embodiment 6 FIG. FIG. 13 shows the sixth embodiment. 12c is a flat portion provided on the orbiting small diameter portion 12a, 15c is a second concave portion, and 15d is a second concave portion 15.
c is a flat portion. The other structures of the compressor are the same as those shown in FIG. 6 and the like.
And so on.

Next, the operation will be described. During operation of the compressor, a force for rotating the sleeve 14 with respect to the swing shaft 12 acts between the swing bearing 6 and the sleeve 14 due to friction. This acting force is transmitted to the engaging member 15, and the engaging member 1
A torque is generated to rotate 5 relative to swing shaft 12. In the present embodiment, since the torque is transmitted between the flat portion 12c and the flat portion 15d, there is no need to transmit the torque with the fastening member 20, and there is no problem such as loosening or breakage of the fastening member 20, thereby improving reliability. A high scroll compressor can be obtained.

[0030]

As described above, in the scroll compressor according to the first aspect of the present invention, the swing shaft is fitted to the swing bearing via the sleeve, and the sleeve is engaged. While being connected so that it rotates integrally with the swing shaft by a member,
Rotatably fitted to the swing shaft, corresponding to the axial center of the swing bearing, the outer peripheral surface of the swing shaft, or,
Corresponding to the axial center portion of the rocking bearing, a belt-shaped convex portion is provided on the inner peripheral surface of the sleeve over the entire circumference in a direction perpendicular to the axial direction, so that the rocking shaft bends or tilts. Even so, it is possible to provide a highly reliable scroll compressor in which the sleeve is kept parallel to the swing bearing, the bearing load capacity of the swing bearing does not decrease, and the swing bearing is not damaged. it can.

The scroll compressor according to a second aspect of the present invention is the scroll compressor according to the first aspect, wherein an oil reservoir for lubricating oil is provided at a lower portion of the closed vessel, an oil pump is provided at a lower portion of the crankshaft, and provided inside the crankshaft. An oil passage communicating the eccentric hole and the oil pump, and an oil groove provided in the swing bearing, and a substantially disc-shaped engaging member having at least one projection is fixed to the lower end of the swing shaft, A notch of finite depth is provided at the lower end on the inner peripheral side of the sleeve, and the sleeve and the swing shaft are connected in the rotational direction with the protrusion and the notch, and the notch bottom of the sleeve is connected to the notch. Since it was seated on the projection of the engagement member,
A space can be secured at the bottom of the eccentric hole, and an oil supply path to the oscillating bearing can be secured, so that lubricating oil can be reliably supplied to the oscillating bearing. As a result, a scroll compressor with higher bearing reliability can be obtained.

The scroll compressor according to a third aspect of the present invention is the scroll compressor according to the second aspect of the present invention, wherein a lower end portion of the swinging shaft is provided with a orbital small diameter portion smaller than the outer diameter of the circumferential portion of the engaging member. The first concave portion is formed, and a convex portion is provided on the inner peripheral portion of the sleeve, and the sleeve is fitted with the first concave portion with a predetermined axial gap, so that the axial movement of the sleeve is restricted,
In addition to the effects of the second aspect, vibration and noise due to axial movement of the sleeve are reduced, and a low noise and low vibration scroll compressor can be obtained.

Further, in the scroll compressor according to the fourth invention, in the third invention, the dimensional relationship between the axial length L1 of the sleeve and the swing bearing length L2 is set so that L1> L2. In addition, when the sleeve is moved in the axial direction within the axial gap formed by the sleeve convex portion and the first concave portion, the end of the sleeve is prevented from wrapping with the sliding surface of the swing bearing. The movement in the axial direction is restricted, the overlap between the end of the sleeve and the sliding surface of the oscillating bearing is prevented, and in addition to the effects of the third invention, abnormal wear of the oscillating bearing can be prevented, and furthermore, reliability is improved. Scroll compressor with high performance can be obtained.

The scroll compressor according to a fifth aspect of the present invention is the scroll compressor according to the third or fourth aspect, wherein a fastening member for fastening the swing member to the engaging member, and a fastening portion of the engaging member to the swing shaft. And the second concave portion is fitted with the orbital small-diameter portion at the end of the oscillating shaft, so that when the oscillating shaft, sleeve and engagement member are assembled, the orbital small-diameter portion of the oscillating member is used. Can be fitted into the second concave portion of the engagement member to perform positioning, and a scroll compressor with good assemblability can be obtained.

The scroll compressor according to a sixth aspect of the present invention is the scroll compressor according to the fifth aspect, wherein at least one flat portion is provided in the orbiting small diameter portion at the end of the swing shaft, and the second recess of the engagement member is provided in the second recess. Since the flat portion corresponding to the flat portion of the orbital small diameter portion is provided, the torque acting on the engaging member is transmitted by the flat portion at the end of the swing shaft, so that the fastening member is not loosened or damaged,
A highly reliable scroll compressor can be obtained.

[Brief description of the drawings]

FIG. 1 is a sectional view of a main part of a compressor according to Embodiment 1 of the present invention.

FIG. 2 is a perspective view of a sleeve according to the first embodiment of the present invention.

FIG. 3 is a cross-sectional view of a main part of the compressor, illustrating an operation of the first embodiment of the present invention.

FIG. 4 is a sectional view of another compressor main part according to Embodiment 1 of the present invention.

FIG. 5 is a sectional view of still another compressor main part according to Embodiment 1 of the present invention.

FIG. 6 is a sectional view of a compressor according to a second embodiment of the present invention.

FIG. 7 is a sectional view of a main part of a compressor according to a second embodiment of the present invention.

FIG. 8 is a main part drawing of a compressor according to a second embodiment of the present invention.

FIG. 9 is a sectional view of a main part of a compressor according to Embodiments 3 and 4 of the present invention.

FIG. 10 is a cross-sectional view of a main part of a compressor for describing an operation of a fourth embodiment of the present invention.

FIG. 11 is a sectional view of a main part of a compressor according to a fifth embodiment of the present invention.

FIG. 12 is a sectional view of a main part of a compressor according to a fifth embodiment of the present invention.

FIG. 13 is a sectional view of a main part of a compressor according to a sixth embodiment of the present invention.

FIG. 14 is a sectional view showing a conventional scroll compressor.

FIG. 15 is a cross-sectional view of a compressor showing an operation of a conventional scroll compressor.

FIG. 16 is a cross-sectional view showing the operation of a conventional scroll compressor.

[Explanation of symbols]

Reference Signs List 1 oscillating scroll, 3, 4 frame, 5 fixed scroll, 6 oscillating bearing, 7, 11 bearing, 8 closed vessel, 9 motor (rotor), 10 crankshaft, 10a
Eccentric hole portion, 12 swing shaft, 12a orbiting small diameter portion, 12
b first concave portion, 12c flat portion, 13 band-shaped convex portion,
14 sleeve, 14a notch, 14b sleeve convex portion, 15 engaging member, 15a projection, 15c second concave portion, 15d flat portion, 16 oil pump, 17 oil reservoir, 18 oil passage, 20 fastening member.

Claims (6)

[Claims] An oscillating scroll for compressing a fluid in combination with an airtight container, a fixed scroll on which a spiral wrap is provided, and a spiral wrap provided on the spiral wrap of the fixed scroll. A swing shaft provided on the opposite side of the spiral wrap of the swing scroll, a crankshaft rotated by an electric motor, a frame having a bearing for rotatably supporting the crankshaft, and a crankshaft. A scroll compressor comprising: an eccentric hole provided at one end of the eccentric hole; and an oscillating bearing formed on an inner peripheral surface of the eccentric hole, wherein the oscillating shaft is connected to the oscillating bearing by the thread. And the sleeve is connected so as to rotate integrally with the swing shaft by an engagement member, and is fitted rotatably to the swing shaft. Corresponding to the central part in the axial direction, the outer peripheral surface of the swing shaft or the swing Corresponds to the axial center of the bearing, the Sri - scroll, characterized in that a strip-shaped convex portions over the entire circumference on the inner peripheral surface is convex in the axial direction and vertical blanking - Le compressor. 2. An oil reservoir for lubricating oil at a lower portion of a sealed container, an oil pump provided at a lower portion of the crankshaft, an oil passage provided inside the crankshaft and communicating an eccentric hole with the oil pump, and a rocking bearing. A substantially disc-shaped engaging member having at least one projection is fixed to the lower end of the swing shaft, and has a finite depth at the lower end on the inner peripheral side of the sleeve. A notch is provided, the sleeve and the pivot are connected in the rotational direction with the protrusion and the notch, and the notch bottom of the sleeve is seated on the protrusion of the engagement member. The scroll compressor according to claim 1, wherein 3. A swinging small-diameter portion which is smaller than an outer diameter of a circumferential portion of an engaging member is provided at a lower end of a pivot shaft to form a first concave portion in cooperation with the engaging member and an inner circumferential portion of a sleeve. 3. A scroll compressor according to claim 2, wherein a convex portion is provided on said first concave portion, and said first concave portion is fitted with a predetermined axial gap. 4. The dimensional relationship between the axial length L1 of the sleeve and the swing bearing length L2 is set so that L1> L2, and the sleeve is formed of a sleeve having a convex portion and a first concave portion. The scroll compressor according to claim 3, wherein the end of the sleeve does not overlap with the sliding surface of the swing bearing when the sleeve moves in the axial direction within the gap. 5. A fastening member for fastening the swinging shaft and the engaging member, and a second recessed portion provided in a fastening portion of the engaging member with the swinging shaft,
5. The scroll compressor according to claim 3, wherein a small-diameter portion around the end of the pivot shaft and a second recess are fitted. 6. The method according to claim 6, wherein at least one flat portion is provided in the orbiting small diameter portion at the end of the swing shaft, and a flat portion corresponding to the flat portion of the orbiting small diameter portion is provided in the second concave portion of the engaging member. The scroll compressor according to claim 5, wherein