JPH04284193A - Scroll compressor - Google Patents

Abstract

PURPOSE:To simplify bearing parts, spread a thrust receiving surface, facilitate adjustment of a movable gap, prevent the friction of a slidable part, and reduce input. CONSTITUTION:An annular thrust bearing 26 which supports the surface an the turning driving shaft 25 side of the turning end plate 19 of a turning scroll part 20 is arranged as separated part on a bearing part 6, and the inside diameter of the thrust bearing 26 is made smaller than the outside diameter of the main shaft of a rotary shaft 11.

Description

[Detailed description of the invention]

0001

BACKGROUND OF THE INVENTION 1. Field of the Invention This invention relates to a scroll compressor.

0002

[Prior Art] Conventionally, scroll compressors were
The structure is as shown in Japanese Patent No. 28782, and its structure will be explained below with reference to FIG.

As shown in the figure, a compression mechanism 102 is fixed inside an airtight container 101, a stator 103 of an electric motor is fixed below the compression mechanism 101, and a lubricating oil reservoir 104 for storing lubricating oil is further below the compression mechanism 102.
is provided. The airtight container 101 includes the airtight container 10
A generally disc-shaped bearing component 106 that divides the inside of the compressor 1 into a drive chamber 105A and a compression mechanism chamber 105B is integrally fixed, and the drive chamber 105A and compression mechanism chamber 105B communicate with each other. A communication hole 107 is provided. Further, at a position away from the communication hole 107, a sealed container 10 is provided.
A communication path 109 in the shape of a cutout groove is formed to communicate the discharge pipe 108 provided in the drive chamber 105A with the drive chamber 105A.

As described above, the stator 103 of the electric motor is integrally attached to the sealed container 101 in the drive chamber 105A, and the rotor 110 is vertically and rotatably supported in the center of the bearing component 106. It is integrally attached to the rotating shaft 111. The lower end of the rotating shaft 111 is submerged in the lubricating oil reservoir 104 at the bottom of the closed container 101, and the lubricating oil suction hole 11 provided at the axial center of the rotating shaft 111
Each part is supplied with oil through 2.

[0005] The compression mechanism section 102 includes the compression mechanism chamber 10.
5B, a fixed scroll component 115 having a fixed scroll 113 integrally formed on a disk-shaped fixed end plate 114, and an orbiting scroll that meshes with the fixed scroll 113 to form a plurality of compressed spaces 117. 118 is composed of an orbiting scroll component 120 formed on a disc-shaped orbiting mirror plate 119.

The fixed end plate 114 has a plurality of bolts 12.
1, the fixed head plate 114 has a discharge port 12 that discharges compressed high-pressure gas into the compression mechanism chamber 105B.
2 is drilled. Further, in a portion corresponding to the outermost side of the compression space 117 formed by joining the fixed scroll 113 or the fixed end plate 114 and the orbiting scroll 118, the fixed end plate 114 has a structure for sucking gas. A suction port 123 is provided, and a suction pipe 124 is connected to the suction port 123.

The rotating end plate 119 is combined with the fixed end plate 114 in order to form the compressed spaces 117 at a plurality of locations by the integrally provided rotating scroll 118 slidingly contacting the fixed scroll 113 at a plurality of locations. be. A cylindrical fitting part 125 is formed in the center of the back surface of the rotating mirror plate 119, and the eccentric part 111E of the rotating shaft 111 is rotatably fitted into the fitting part 125. be. Further, the back surface of the rotating mirror plate 119 is slidably supported on the end surface of an annular projection 126 formed integrally with the bearing component 106. A low pressure chamber 127 is formed outside the protrusion 126 and is freely communicable with the suction chamber 116. A rotation restraint component 128 is disposed within the low pressure chamber 127.

The rotation restraint component 128 is the fixed end plate 1
The rotating head plate 119 always maintains a constant directionality with respect to the rotation restraining part 14.
A lower protruding line 128L in the radial direction is formed on the lower surface of 28, and an upper protruding line (not shown) is formed on the upper surface in a direction perpendicular to the lower protruding upper part 128L. The lower protrusion 128L of the rotation restraint component 128 is slidably engaged with a guide groove 129 formed at the bottom of the low pressure chamber 127, and the upper protrusion is engaged with a guide groove formed on the back surface of the rotating mirror plate 119. 130 in a slidable manner.

In the above configuration, when the rotating shaft 111 is rotated by the electric motor, the eccentric portion 111E of the rotating shaft 111 rotates eccentrically. Therefore, the rotating mirror plate 119 is rotated while its directionality is kept constant by the rotation restraining component 128. At this time, the compressed space 117 gradually moves from the outer circumferential side to the inner circumferential side, and the compressed space 117 is gradually reduced. Therefore, the gas in the compression space 117 is compressed and discharged from the discharge port 122 to the compression mechanism chamber 105B.

The high pressure gas discharged into the compression mechanism chamber 105B passes through the communication hole 107 and enters the drive chamber 105A.
The liquid is then discharged from the discharge pipe 108 to the outside.

As described above, when the rotating head plate 119 is rotated by the electric motor to compress the gas, the compression is performed from the suction port 123 via the gas suction pipe 124. Also,
Since the high pressure gas is discharged into the closed container 101, the inside of the closed container 101 becomes high pressure, and this high pressure acts on the back surface of the rotating mirror plate 119. However, since the annular protrusion 106 formed on the bearing component 106 abuts and supports the back surface of the rotating mirror plate 119, and the outside of the protrusion 126 is formed in the low pressure chamber 127, the protrusion 126 High pressure is applied to the rotating mirror plate 119 only on the inside of the rotating mirror plate 119. Therefore, the pressing force for pressing the rotating end plate 119 toward the fixed end plate 114 can be reduced to some extent.

However, due to the pressure in the compressed space 117, the rotating mirror plate 119 receives a force in a direction that moves it away from the fixed mirror plate 114, but the distribution of the force is different from that of the rotating mirror plate 11.
Since the center portion of the protrusion 9 is larger than the outer circumference thereof, the diameter of the protrusion 126 must be appropriately set in consideration of the above pressure distribution.

The axial movable clearance of the orbiting scroll component 120 is adjusted by the difference between the depth of the annular protrusion 126 from the end surface of the bearing component 106 and the thickness of the orbit mirror plate 119.

[0014]

[Problems to be Solved by the Invention] In such a conventional scroll compressor, the part that supports the back surface of the rotating head plate is integrated with the bearing component 106, and is provided as an annular protrusion 126 on the outer periphery of the rotating shaft 111. Since it is necessary to arrange the rotation restraining part 128 and secure a space for movement, if the supporting part cannot be made large and thrust force is applied to the rotating head plate 119, the load due to the thrust force becomes large and the supporting part wears out. becomes larger, or the input due to friction increases. In addition, the support part of the rotating head plate 119 is connected to the bearing part 10.
6, the shape of the bearing component 106 becomes complicated and the supporting portion cannot be made large, making it difficult to adjust the movable clearance in the axial direction of the orbiting scroll component 120.

Furthermore, since the supporting portion cannot be made large, reliable sealing between high and low pressures on the inner and outer peripheries of the supporting portion cannot be achieved. Even if a sealing material is used to seal high and low pressures, the diameter of the groove into which the sealing material is inserted cannot be freely selected so as to optimize the pressure distribution acting on the rotating head plate. Therefore, it is difficult to adjust the pressure distribution acting on the swiveling head plate 119, and the load increases, resulting in wear of the support portion and an increase in input power.

[0016]

[Means for Solving the Problems] The first technical means for solving the problems of the conventional scroll compressor described above is to arrange an electric motor and a compression mechanism driven by the electric motor inside a closed container. a fixed scroll component having a fixed scroll in which the compression mechanism is fixed or formed integrally with a fixed end plate, and an orbiting scroll that engages with the fixed scroll and forms a plurality of compression spaces, fixed or formed on the orbiting end plate. an orbiting scroll component, a rotation restraint component that restrains rotation of the orbiting scroll component, a rotating shaft that eccentrically drives the orbiting scroll component, and a bearing component that supports a main shaft formed at one end of the rotating shaft. The orbiting drive shaft formed on the opposite side of the orbiting scroll of the orbiting mirror plate is fitted into an eccentric bearing provided eccentrically inside the main axis of the rotating shaft, and the orbiting drive shaft of the orbiting mirror plate of the orbiting scroll component An annular thrust bearing that supports the surface on the swing drive shaft side is disposed as a separate part in the bearing component, and the inner diameter of the thrust bearing is configured to be smaller than the main shaft outer diameter of the rotating shaft. A second technical means for solving the problem is, in addition to the first solving means,
A groove that communicates only with the inner circumferential side or the outer circumferential side on the surface of the thrust bearing that supports the orbiting scroll component, or
This means that grooves that communicate between the inner and outer circumferential sides are provided in a radial or spiral shape. A third technical means for solving the problem, in addition to the first solution, is to reduce the thickness from the inner circumference of the thrust bearing to a portion with a diameter equivalent to the main shaft outer diameter of the rotating shaft at the outer circumference. It is to make it thinner than the thickness of . A fourth technical means for solving the problem, in addition to the first solution described above, is to configure the thrust bearing with wear-resistant sintered iron.

A fifth technical means for solving the problem is that an electric motor and a compression mechanism driven by the electric motor are disposed inside a closed container, and the compression mechanism is fixed or formed integrally with a fixed head plate. A fixed scroll component having a fixed scroll, an orbiting scroll component in which an orbiting scroll that meshes with the fixed scroll and forms a plurality of compression spaces is fixed or formed on an orbiting head plate, and an autorotation that restrains the rotation of the orbiting scroll component. A restraining component, a rotating shaft for eccentrically rotating the orbiting scroll component, and a bearing component for supporting a main shaft formed at one end of the rotating shaft, and formed on the opposite side of the orbiting mirror plate from the orbiting scroll. The rotating drive shaft is fitted into an eccentric bearing provided eccentrically inside the main shaft of the rotating shaft, and an annular plate that supports the surface of the rotating head plate of the orbiting scroll component on the side of the rotating drive shaft is provided as a separate part. placed on the bearing component as
The inner diameter of the plate is configured to be smaller than the outer diameter of the main shaft of the rotating shaft, and an annular groove for inserting a sealing material is provided on the surface facing the orbiting scroll component, and the sealing material is inserted therein. A sixth technical means for solving the problem, in addition to the fifth solving means, is to configure the plate as a thrust bearing to receive the thrust load of the orbiting scroll component. In addition to the fifth solution, a seventh technical means for solving the problem is to provide grooves that communicate only with the inner circumferential side or the outer circumferential side in a radial or spiral manner on the surface of the plate facing the orbiting scroll component. It is to be provided in the form of In addition to the fifth solution, an eighth technical means for solving the problem is to reduce the thickness from the inner periphery of the plate to the portion with a diameter equivalent to the main shaft outer diameter of the rotating shaft by reducing the thickness of the outer periphery. The goal is to make it thinner than it is.

[0018]

[Operation] The operation of the first technical means of the present invention described above is as follows:
By arranging a thrust bearing that receives the thrust force of the orbiting scroll component on the orbiting drive shaft side of the orbiting head plate of the orbiting scroll component, and making the inner diameter of the thrust bearing smaller than the outer diameter of the main shaft of the rotating shaft, the thrust bearing surface can be enlarged. In addition, the axial movable clearance of the orbiting scroll component can be easily adjusted, and the shape of the bearing component can also be simplified. The effect of the second technical means is to improve the lubrication of the thrust bearing surface by providing oil grooves in the thrust bearing. The third technical means works by making the thickness of the part from the inside diameter of the thrust bearing to the diameter equivalent to the outside diameter of the main shaft of the rotating shaft thinner than the thickness of the outer circumference, while maintaining a wide thrust bearing surface. The distance between the orbiting scroll component and the rotating shaft can be shortened, the moment force of whirling of the orbiting scroll component can be reduced, and the force applied to the thrust surface can be reduced. The effect of the fourth technical means is that since the thrust bearing is a separate component from the bearing components, sintered iron with good wear resistance can be used and reliability can be improved. The effect of the fifth technical means is to provide an annular plate facing the surface of the orbiting drive shaft side of the orbiting end plate of the orbiting scroll component, and to make the inner diameter of the annular plate smaller than the outer diameter of the main shaft of the rotating shaft. By providing an annular groove for inserting a sealing material on the opposite surface and inserting the sealing material, the pressure distribution on the inner and outer peripheries of the sealing material can be adjusted with the sealing material, and the diameter of the annular groove can be freely selected. The effect of the sixth technical means is that by configuring the annular plate as a thrust bearing to receive the thrust load of the orbiting scroll component, the two functions of pressure distribution adjustment and thrust bearing can be easily configured in one component. It is possible. The effect of the seventh technical method is that by providing an oil groove on the surface of the annular plate facing the orbiting scroll component, the sliding part between the plate and the orbiting scroll component is lubricated, and the sealing part by the sealing material is Being able to refuel. The effect of the eighth technical method is to maintain a wide flat area by making the thickness of the part from the inner diameter of the annular plate to the diameter equivalent to the outer diameter of the main shaft of the rotating shaft thinner than the thickness of the outer peripheral part. The distance between the orbiting scroll component and the rotating shaft can be shortened, the moment force of whirling of the orbiting scroll component can be reduced, and the force applied to the thrust surface can be reduced.

[0019]

Embodiment An embodiment of the present invention is shown in FIGS. 1 to 3.

As shown in the figure, a compression mechanism 2 and a stator 3 of an electric motor are fixed to the inside of a closed container 1, and a lubricating oil reservoir 4 for storing lubricating oil is provided below the compressing mechanism 2. A generally disc-shaped bearing part 6 that divides the inside of the sealed container 1 into a drive chamber 5A and a compression mechanism chamber 5B is integrally fixed to the sealed container 1. A communication hole 7 communicating with the compression mechanism chamber 5B is provided. Further, at a position away from the communication hole 7, a discharge pipe 8 is formed in the closed container 1 and communicates with the drive chamber 5A. As described above, the stator 3 of the electric motor is integrally attached to the sealed container 1 in the drive chamber 5A, and the rotor 10 is a rotary motor supported perpendicularly and rotatably in the center of the bearing component 6. It is integrally attached to the shaft 11. The lower end of the rotating shaft 11 is
It is submerged in a lubricating oil reservoir 4 at the bottom of the closed container 1, and each part is supplied with lubricating oil through a lubricating oil suction hole 12 provided at the axial center of the rotating shaft 11.

The compression mechanism section 2 is disposed in the compression mechanism chamber 5B, and includes a fixed scroll component 15 having a fixed scroll 13 integrally formed on a disk-shaped fixed end plate 14, and the fixed scroll 13. An orbiting scroll component 20 in which an orbiting scroll 18 that meshes with each other to form a plurality of compression spaces 17 is formed on a disc-shaped orbiting end plate 19.
It is composed of etc.

The fixed end plate 14 is closely fixed to the bearing component 6 by a plurality of bolts 21, and a compressed high pressure gas is discharged into the compression mechanism chamber 5B at approximately the center of the fixed end plate 14. A discharge port 22 is provided. Further, the fixed scroll 13 or the fixed end plate 1
4 and the orbiting scroll 18, a suction port 23 for sucking gas is bored in the fixed end plate 14 at a position corresponding to the outermost side of the compression space 17 formed by the joining of the orbiting scroll 18 and the orbiting scroll 18, A suction pipe 24 is connected to this suction port 23.

The rotating end plate 19 is combined with the fixed end plate 14 in order to form the compressed spaces 17 at a plurality of locations by the integrally provided rotating scroll 18 slidingly contacting the fixed scroll 13 at a plurality of locations. be. A turning drive shaft 25 is provided on the surface of the turning mirror plate 19 opposite to the turning scroll 18, and is rotatably fitted into the eccentric drive bearing 11E of the rotating shaft 11.

Further, the surface of the rotating mirror plate 19 on the rotating drive shaft side is slidably supported on the end surface of an annular plate 26 formed as a separate component from the bearing component 6. The annular plate 26 has an inner diameter smaller than an outer diameter of the main shaft of the rotating shaft 11 to ensure a large sliding surface. A low pressure chamber 27 is formed on the outside of the annular plate 26 and is freely communicable with the suction chamber 16. A rotation restraint component 28 is disposed within the low pressure chamber 27. The rotation restraint part 2
Reference numeral 8 serves to always keep the directionality of the rotating head plate 19 constant with respect to the fixed head plate 14, and a radial upper protrusion 28U is formed on the upper surface of the rotation restraining part 28. A lower protrusion (not shown) is formed on the lower surface in a direction perpendicular to the upper protrusion 28U. The lower protrusion of the rotation restraint component 28 is slidably engaged with a guide groove (not shown) formed at the bottom of the low pressure chamber 27, and the upper protrusion 28U is formed on the back surface of the rotating mirror plate 19. The guide groove 30 is slidably engaged with the guide groove 30 . In the above configuration, when the rotating shaft 11 is rotated by the electric motor, the eccentric bearing portion 11E of the rotating shaft 11 rotates eccentrically. Therefore, the rotating mirror plate 19 is rotated while its directionality is kept constant by the rotation restraining component 28. At this time, the compression space 17 gradually moves from the outer circumference side to the inner circumference side, and the compression space 17 is gradually reduced. Therefore, the gas in the compression space 17 is compressed, and from the discharge port 22 to the compression mechanism chamber 5B.
is discharged to. The high-pressure gas discharged into the compression mechanism chamber 5B passes through the communication hole 7, reaches the drive chamber 5A, and is discharged from the discharge pipe 8 to the outside. As mentioned above, when the rotating head plate 19 is rotated by the electric motor to compress the gas, the compression is performed from the suction port 23 via the gas suction pipe 24. Further, since high pressure gas is discharged into the closed container 1, the inside of the closed container 1 becomes high pressure, and this high pressure acts on the back surface of the rotating mirror plate 19. However, since the annular plate 26 abuts and supports the back surface of the rotating head plate 19, and the outside of the annular plate 26 is formed into the low pressure chamber 27, the turning occurs only on the inside of the annular plate 26. High pressure will act on the end plate 19. Therefore, the pressing force for pressing the swivel head plate 19 toward the fixed head plate 14 can be reduced, and depending on the inner diameter of the annular plate 26 and the pressure in the compressed space 17, the swivel head plate 19 can be pressed against the fixed head plate 14.
However, in this case, the annular plate has a wide thrust bearing surface as described above, and therefore fully functions as a thrust bearing.

Further, the movable clearance in the axial direction of the orbiting scroll component 20 is adjusted by the difference between the depth from the end surface of the bearing component 6 to the end surface of the annular plate 26 and the thickness of the orbit mirror plate 19. Therefore, the annular plate 26
Since the end face is wide and it is a separate part from the bearing part 6, the clearance can be easily adjusted and the shape of the bearing part 6 can be simplified. Furthermore, it is also possible to use a different material for the annular plate 26 than for the bearing part 6, for example sintered iron with high wear resistance.

In addition, in this embodiment, the annular plate 26 is designed to ensure high and low pressure sealing on the inner and outer peripheries, and to adjust the pressure distribution acting on the rotating head plate 19 almost fixedly. An annular groove 26A for inserting a sealing material 31 is formed in the end surface of the plate 26 on the side of the rotating mirror plate 19, and the sealing material 31 is inserted therein. Since the flat portion is wide, the diameter of the annular groove 26A for inserting the sealing material 31 can be optimally selected according to the adjustment of pressure distribution. At the same time, radial oil grooves 26B are formed for lubrication of the sliding parts.

Furthermore, in this embodiment, if the annular plate 26 is formed to have a uniform thickness, the distance between the rotating mirror plate 19 and the eccentric drive bearing 11E of the rotating shaft 11 becomes too large, and the rotating scroll component Since the whirling moment of the plate 20 increases, the thickness from the inner diameter of the annular plate 26 to the portion of the diameter corresponding to the main shaft outer diameter of the rotating shaft 11 is made thinner than the thickness of the outer peripheral portion.

[0028]

As described above, the first effect of the present invention is that the annular thrust bearing that supports the surface of the orbiting end plate of the orbiting scroll component on the orbiting drive shaft side is disposed as a separate component in the bearing component; By configuring the inside diameter of the thrust bearing to be smaller than the outside diameter of the main shaft of the rotating shaft, the surface that receives the thrust force from the orbiting scroll component can be increased, and it is possible to prevent wear of the sliding part and reduce input power. In addition, since the thrust bearing is a separate part from the bearing parts, the axial movable clearance of the orbiting scroll parts can be easily adjusted, allowing the orbiting scroll parts to move without twisting and minimizing gas leakage from the top surface of the scroll. It is possible to set the gap to reduce the gap, improving compressor performance. Furthermore, the shape of the bearing parts can also be simplified.

The second effect of the present invention is that the surface of the thrust bearing that supports the orbiting scroll component can be enlarged, so that grooves for passing lubricating oil can be provided on this surface, thereby improving the lubrication of the sliding surface. It has the effect of preventing wear and reducing input.

A third effect of the present invention is that by making the thickness from the inner circumference of the thrust bearing to the diameter equivalent to the outer diameter of the main shaft of the rotating shaft thinner than the thickness of the outer circumference, a wide thrust surface can be maintained. However, since the rotating shaft can be brought close to the orbiting scroll component, the moment that tends to tilt the rotating shaft due to the orbiting motion of the orbiting scroll component can be suppressed to a small level, and as a result, the thrust bearing part and the rotating shaft can be supported. This means that twisting of the bearing can be suppressed, damage or wear to the bearing can be suppressed, the reliability of the compressor can be improved, and the overall length in the axial direction can be shortened.

A fourth effect of the present invention is that by configuring the thrust bearing as a separate component from the bearing parts, the material of the thrust bearing can be freely selected, so wear-resistant materials can be used, and reliability can be improved. This is something that can be improved.

A fifth effect of the present invention is that an annular plate that supports the surface of the rotating head plate of the orbiting scroll component on the rotating drive shaft side is arranged as a separate component on the bearing component, and the inner diameter of the plate is set to the The outer diameter of the rotary shaft is smaller than the main shaft outer diameter of the rotary shaft, and an annular groove for inserting the sealing material is provided on the surface facing the orbiting scroll component, and the sealing material is inserted. The area of the high and low pressure regions acting on the back surface of the rotating mirror plate can be adjusted, and the surface facing the rotating scroll component is wide, so the insertion position of the sealing material can be selected from a wide range. Therefore, the thrust force (the resultant force of the axial gas pressures acting from each direction) acting on the swivel head plate can be optimally adjusted, making it possible to prevent wear on the sliding parts and reduce input.

The sixth effect of the present invention is that by configuring the annular plate as a thrust bearing, in addition to the fifth effect, the thrust surface can be widened, which reduces wear on the sliding parts and reduces input. It is possible.

A seventh effect of the present invention is that by providing a groove on the surface of the annular plate facing the orbiting scroll component, the sealing performance of the sealing material can be improved, and the height and low pressure acting on the orbiting scroll component can be improved. It is possible to ensure a reliable pressure range and to maintain good lubrication of sliding surfaces, which has the effect of preventing wear and reducing input.

An eighth effect of the present invention is that the thickness from the inner circumference of the annular plate to the diameter equivalent to the outer diameter of the main shaft of the rotating shaft is
By making it thinner than the thickness of the outer circumference, the rotating shaft can be brought closer to the orbiting scroll component while maintaining a wide sealing material insertion surface, which prevents the rotating shaft from tilting due to the orbiting movement of the orbiting scroll component. The moment can be suppressed to a small level, and as a result, the twisting of the thrust bearing and the bearing that supports the rotating shaft is suppressed, and damage and wear can be suppressed, improving the reliability of the compressor and shortening the overall length in the axial direction. Therefore, the compressor can be made smaller.

[Brief explanation of the drawing]

FIG. 1 is a sectional view of an embodiment of a scroll compressor according to the present invention.

FIG. 2 is an exploded perspective sectional view of an embodiment of the annular plate according to the present invention.

FIG. 3 is a perspective view of another embodiment of the annular plate according to the present invention.

[Figure 4] Cross-sectional view of a conventional scroll compressor

[Explanation of symbols]

1　Airtight container 6 Bearing parts 11 Rotation axis 15 Fixed scroll parts 19 Swivel mirror plate 20 Orbiting scroll parts 26 Annular plate 26A Annular groove 26B Radial oil groove 26C Spiral oil groove 27 Low pressure chamber 31 Seal material

Claims (8)

[Claims] 1. A fixed scroll component having a fixed scroll in which an electric motor and a compression mechanism driven by the electric motor are disposed inside an airtight container, and the compression mechanism is fixed or formed integrally with a fixed end plate; an orbiting scroll component having an orbiting scroll fixed or formed on an orbiting end plate that meshes with the orbiting scroll to form a plurality of compressed spaces; a rotation restraint component that restrains the rotation of the orbiting scroll component; and an eccentric rotation drive for the orbiting scroll component. a rotating shaft formed at one end of the rotating shaft, and a bearing part supporting the main shaft formed at one end of the rotating shaft, and a rotating driving shaft formed on the opposite side of the rotating head plate from the rotating scroll. An annular thrust bearing that fits into an eccentric bearing provided eccentrically on the inside and supports a surface of the orbiting head plate of the orbiting scroll component on the orbit drive shaft side is disposed as a separate component in the bearing component, and the thrust bearing A scroll compressor having an inner diameter smaller than an outer diameter of the main shaft of the rotating shaft. [Claim 2] A claim in which a groove that communicates only with the inner circumferential side or the outer circumferential side, or a groove that communicates between the inner circumferential side and the outer circumferential side is provided in a radial or spiral shape on the surface of the thrust bearing that supports the orbiting scroll component. Scroll compressor according to item 1. 3. The scroll compressor according to claim 1, wherein the thickness from the inner periphery of the thrust bearing to a portion with a diameter equivalent to the outer diameter of the main shaft of the rotating shaft is thinner than the thickness of the outer periphery. 4. The scroll compressor according to claim 1, wherein the thrust bearing is made of sintered iron. 5. A fixed scroll component having a fixed scroll in which an electric motor and a compression mechanism driven by the electric motor are disposed inside an airtight container, and the compression mechanism is fixed or formed integrally with a fixed end plate; an orbiting scroll component having an orbiting scroll fixed or formed on an orbiting end plate that meshes with the orbiting scroll to form a plurality of compressed spaces; a rotation restraint component that restrains the rotation of the orbiting scroll component; and an eccentric rotation drive for the orbiting scroll component. a rotating shaft formed at one end of the rotating shaft, and a bearing part supporting the main shaft formed at one end of the rotating shaft, and a rotating driving shaft formed on the opposite side of the rotating head plate from the rotating scroll. An annular plate that fits into an eccentric bearing provided eccentrically on the inside and supports a surface of the orbiting end plate of the orbiting scroll component on the orbiting drive shaft side is disposed as a separate component on the bearing component, and the inner diameter of the plate is a scroll compressor configured to have a diameter smaller than the main shaft outer diameter of the rotating shaft, an annular groove for inserting a sealing material on a surface facing the orbiting scroll component, and a sealing material inserted into the annular groove. 6. The scroll compressor according to claim 5, wherein the plate is configured as a thrust bearing to receive the thrust load of the orbiting scroll component. 7. The scroll compressor according to claim 5, wherein the surface of the plate facing the orbiting scroll component is provided with radial or spiral grooves that communicate only with the inner circumferential side or the outer circumferential side. 8. The scroll compressor according to claim 5, wherein the thickness from the inner periphery of the plate to the portion with a diameter equivalent to the outer diameter of the main shaft of the rotating shaft is thinner than the thickness of the outer periphery.