JPH08159052A - Scroll compressor - Google Patents

Abstract

PURPOSE: To provide a scroll compressor realizing the reduction of cost by simplifying the structure and improving the reliability. CONSTITUTION: A driving pin 15 pressed to be fixed in an eccentric hole 20 of an eccentric bush 19 rotatably supported in a boss 11 of a swirl scroll blade parat 7 through a revolving bearing 12 is rotatably fitted and connected to an eccentric driving hole 18 provided on the end surface of a main shaft 16 with eccentricity, and the eccentric bush 19 is adapted to swing on the driving pin 15 to vary the turning radius, whereby the positions of centers of the eccentric driving hole 18 and the eccentric hole 20 of the eccentric bush, that is, the position of the center of the driving pin 15 is limited within the second quadrant of a definition coordinate.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a drive structure for a scroll compressor used in air conditioners, refrigerators and the like.

[0002]

2. Description of the Related Art As a recent compressor, a scroll compressor has become mainstream from the viewpoints of small size, light weight, high efficiency, low noise and the like. Scroll compressors are disclosed in many patents and documents, and their operating principles are well known.

As a conventional example of the structure of a typical scroll type compressor, there is a scroll type fluid machine of Japanese Examined Patent Publication No. 57-49721, which is a blade-radial follower mechanism of a link coupling for making a spiral vane follow and contact in the radial direction. The technology is disclosed.

In Japanese Patent Publication No. 58-19875, there is disclosed a technique of an eccentric bush mechanism, which is a development of a link-coupling blade radial direction tracking mechanism.

FIG. 7 shows a sectional view of a conventional compressor using this eccentric bush mechanism. At the rear end of the compressor housing 101, a fixed spiral vane component 102 having fixed spiral vanes 104 formed on a fixed mirror plate 103 is fixed, and swirled on a swivel mirror plate 107 so as to form a plurality of compression work spaces 105. Swirling spiral blade component 10 in which spiral blade 108 is formed
6 is engaged. A cylindrical boss 109 is formed on the rear surface of the swirl end plate 107 on the side opposite to the swirl vane 108, and a swirl bearing 110 is disposed inside the cylindrical boss 109. A thick disk-shaped or short-axis eccentric bush 111 having an eccentric hole 112 is rotatably supported in a boss 109 of a swirl spiral blade component 106 via a swirl bearing 110. The drive pin 115 axially and eccentrically extended from the end surface of the main shaft 114 is provided with the eccentric hole 11 of the eccentric bush 111.
2 is rotatably fitted to impart a swirling motion to the swirling spiral vane component 106. On the other hand, the torque is transmitted to the main shaft 114 via the shaft sealing device 117.
1. An electromagnetic clutch 118 attached to the end of the main shaft 114 protruding to the outside causes rotation of an external drive source (for example, an automobile engine, not shown) via a transmission means (not shown) such as a belt.

In the structure of such a drive mechanism, when the main shaft 114 rotates, the center of the eccentric bush 111 swings in an arc around the center of the drive pin 115 due to the action force such as the fluid compression gas force. As a result, the swirling spiral blade 108 follows the fixed spiral blade 104 and comes into contact with the fixed spiral blade 104 to improve the radial sealing performance of the compression work space 105.

On the turning end plate 107, a turning side race 119 and a turning side retainer 120 made of high hardness steel are arranged.
Step 12 provided on the inner wall of the front part of the compressor housing 101
1, a fixed side race 122 and a fixed side retainer 123 are arranged, and a thrust force applied to the turning end plate 107 by sandwiching a large number of steel balls 124 in both the races and the retainers in the axial direction and the turning radial direction. And the rotation of the swirling spiral blade part 106 is restrained.

In this conventional compressor, the position of the drive pin 115 is limited. By limiting the position to this position, when a sudden increase in acceleration occurs at the time of starting,
Due to the inertial force of the swiveling component, the center of the eccentric bush 111 swings in a direction in which the contact portions of both blades are separated and the pressure in the compression work space 105 is released. As a result, it is possible to prevent the occurrence of abnormal noise and shock at the time of starting.

Further, the eccentric bush 111 is a drive pin 11.
Since it can rotate around 5, it has the above-mentioned radial sealing effect, but it is necessary to limit the rotation angle range associated with the swing of the eccentric bush 111 in order to solve problems such as interference with surrounding parts. As a means for limiting the rotation angle range of the eccentric bush 111, the eccentric bush 111 is extended with the restriction pin 113, and the restriction hole 11 is provided in the main shaft 114.
It is configured by fitting into 6 with a predetermined gap.

[0010]

However, in order to eccentrically extend the drive pin 115 from the end portion of the main shaft 114 by integrally molding, a forming method such as forging is used. Since the diameter cannot be made large, it is quite difficult to obtain a near net shape that minimizes material loss. Furthermore, since the drive pin is also finished off-center with respect to the axis of the spindle, it cannot be machined simultaneously with the spindle, which complicates the machining process. Further, in the above-mentioned configuration, it is necessary to provide a rotation angle range limiting means for limiting the rotation angle range in accordance with the swing motion of the eccentric bush 111 in a separate configuration, which is disadvantageous in terms of manufacturing and high in cost.

The present invention solves the problems of the above-mentioned conventional example, and simplifies the structure to realize low cost, and
The object is to provide a scroll compressor having improved reliability.

[0012]

In order to solve the above-mentioned problems, the first technical means of the present invention is to fix a fixed end plate on a fixed end plate so as to form a plurality of compression working spaces in a compressor housing. Fixed swirl vane parts with swirl vanes extended, swirl swirl vane parts extended on the swirl end plate, and swirl swirl vane parts with a boss formed on the surface opposite to the extension surface of the swirl swirl vanes. A swivel bearing provided inside the boss of the swirl spiral vane component, a drive mechanism for imparting swirl motion to the swirl spiral vane component, and an eccentric hole rotatably supported in the boss via the swirl bearing. An eccentric bush having a cylindrical recess having an area larger than the hole area and opening to the spindle side, and a dynamic imbalance of a swivel component attached to a mounting plate integrally formed at an end of the eccentric bush on the spindle side. To reduce A balance weight, a drive pin that is press-fitted and fixed in an eccentric bushing eccentric bush, and a cylindrical portion that fits in a recess of the eccentric bushing with a small gap are formed at the inner end and are rotatably supported by the compressor housing. A main shaft, an eccentric drive hole for rotatably fittingly joining the drive pin provided eccentrically to the end face of the cylindrical portion of the main shaft, and a rotation restraining component for restraining only the rotation of the swirling spiral blade component to rotate. And a line connecting the axis of the main shaft and the center of the eccentric bush is defined as a second coordinate axis.
A line that is perpendicular to the coordinate axes of the eccentric bush and passes through the center of the eccentric bush is defined as a first coordinate axis, and an intersection of the first coordinate axis and the second coordinate axis is defined as an origin of each coordinate axis, and the second coordinate axis is defined. The positive axis on the side opposite to the axis of the main axis with respect to the first coordinate axis and the negative area on the side of the axis, and the first coordinate axis with respect to the rotation direction of the main axis with respect to the second coordinate axis. In order, a region in which the second coordinate axis region changes from negative to positive is defined as a positive region and the opposite side is defined as a negative region, and a quadrant in which the first coordinate axis is positive and the second coordinate axis is positive is a first quadrant, The second quadrant is a quadrant in which the first coordinate axis is negative and the second coordinate axis is positive, and the third quadrant is the quadrant in which the first coordinate axis is negative and the second coordinate axis is negative.
A quadrant in which the first coordinate axis is positive and the second coordinate axis is negative
It is defined as a quadrant, and the centers of the eccentric drive hole and the eccentric hole of the eccentric bush, that is, the center of the drive pin are located in the second quadrant.

A second technical means of the present invention is that the outer peripheral end surface portion of the turning balance weight on the main shaft side is formed into an L-shaped step.

The third technical means of the present invention is to provide a hole in the mounting plate of the turning balance weight integrally formed at the end of the eccentric bush on the main shaft side.

A fourth technical means of the present invention is to provide a through hole inside the drive pin.

[0016]

According to the first technical means of the present invention, the eccentric bush swings around the center of the drive pin located in the second quadrant as the center of rotation by the action of the fluid compression gas force and the centrifugal force. Since the swirling radius is made variable, the swirling spiral vanes follow the fixed swirl vanes following, and good radial sealing performance is obtained in the compression work space as in the conventional compressor. Also,
When the acceleration rapidly increases, such as at the time of starting, the inertial force of the swiveling parts acts to swing the eccentric bush in the direction in which both blades separate, releasing the pressure in the compression work space, and causing abnormal noise or shock at the time of starting. It also has the effect of alleviating liquid compression.

Further, since the separate drive pin is press-fitted and fixed to the eccentric bush, the workability is improved as compared with the conventional compressor. Further, the rotation restriction due to the swing of the eccentric bush is performed between the concave portion of the eccentric bush and the cylindrical portion of the main shaft fitted in the concave portion with a small gap, and the rotation angle range is determined by the small gap provided therebetween. It For this reason, there is no need to provide a rotation angle range limiting means in a separate configuration as in the prior art, and the structure is simplified and the manufacturing cost is reduced.

Further, since the eccentric bush is provided with the cylindrical concave portion which is open to the main shaft side in an area larger than the hole area of the eccentric hole, the center of gravity of the eccentric bush in the axial direction approaches the turning end plate. Therefore, even when the orbiting balance weight is attached to the end face on the main shaft side, it is possible to easily realize that the center of gravity in the axial direction is located near the center of the bearing surface of the orbiting bearing. As a result, tilting of the eccentric bush system during swivel motion can be suppressed, and the reliability of the swivel bearing can be improved.

According to the second technical means of the present invention, the first
In addition to the effect of the technical means of 1., the outer peripheral end surface portion on the main shaft side of the turning balance weight is formed with an L-shaped step so that the center of gravity of the turning balance weight in the axial direction approaches the turning end plate. This is facilitated by locating the axial center of gravity of the eccentric bushing system including the balance weight near the center of the bearing surface of the slewing bearing. The reliability of can be improved.

According to the third technical means of the present invention, the first
In addition to the effect of the technical means described above, a hole is formed in the mounting plate of the swivel balance weight integrally formed at the end of the eccentric bush on the main shaft side to reduce the weight of the mounting plate located outside the bearing surface of the swivel bearing. Since the center of gravity of the eccentric bush system in the axial direction is more easily located near the center of the bearing surface of the slewing bearing,
Furthermore, it suppresses tilting of the eccentric bush system during turning motion,
The reliability of the slewing bearing can be further improved.

According to the fourth technical means of the present invention, the first
In addition to the function of the technical means of (1), the through hole provided inside the drive pin prevents the lubricating oil to the slewing bearing from being retained inside the boss of the swirl spiral vane component, and from the through hole to the inside of the compressor housing. Since the oil is returned to the space, sufficient lubricating oil is secured for the slewing bearing, and the reliability of the slewing bearing is enhanced.

[0022]

FIG. 1 is a sectional view of a scroll compressor and FIG. 2 is an exploded perspective view of a drive mechanism using an eccentric bush as an embodiment using the first technical means of the present invention.

A swirl is performed so as to form a fixed spiral vane component 4 and a plurality of compression working spaces 10 inside a compressor housing 1 consisting of a front casing 2 on which a low pressure is applied and a rear casing 3 on which a high pressure is applied. The spiral vane components 7 are intermeshed with each other.

The fixed spiral blade component 4 has a fixed spiral blade 6 extending on one surface of the fixed mirror plate 5, and is fixedly fastened to the rear casing 3 by this fixed mirror plate surface. Swirling spiral blade parts 7
Has a swirl spiral blade 9 extending over one surface of the swirl mirror plate 8, and a cylindrical boss 11 is projectingly provided in the central portion of the rear surface of the swirl mirror plate 8 on the side opposite to the extending surface of the swirl spiral blade 9. A slewing bearing 12 (needle bearing) is arranged inside the boss 11. The tip seals 13 are fitted and inserted into the tip surfaces of the fixed spiral blade 6 and the swirl spiral blade 9, respectively, to secure the axial sealability.

The swirling motion of the swirling spiral vane component 7 is controlled by a main shaft 16 rotatably supported on the compressor housing 1 by a main bearing 14a and a sub bearing 14b by a swivel radius variable drive mechanism using an eccentric bush 19 described later. Done through. On the other hand, the torque is transmitted to the main shaft 16 by the shaft sealing device 30.
The rotation of the external drive source (not shown) is transmitted by means of an electromagnetic clutch 31 attached to the end of the main shaft 16 protruding outside the compressor housing 1 via a belt (not shown).
Done through.

The swirling spiral blade component 7 is a rotation restraint component 23.
It only makes a turning motion while its rotation is blocked by. The rotation restraint part 23 is formed with a pair of keys 23a parallel to each other on the end surface of its annular body, and a pair of keys 23b parallel to each other at a position shifted by approximately 90 °. The key 23a is slidably fitted into a pair of key grooves 8a formed on the back surface of the swirl end plate 8 of the swirl spiral blade component 7, and the other pair of keys 23b is fitted and fixed inside the compressor housing 1. A pair of key grooves (not shown) formed corresponding to the keys 23b are slidably fitted in the rotation restraint component 24. The rotation restraint component 24 restrains the movement of the rotation restraint component 23 only in one direction perpendicular to the axis of the main shaft 16.

The swirling motion of the swirling spiral vane component 7 causes the compression work space 10 to move toward the center of the spiral while reducing its volume. Along with this, the gas flowing into the compression work space 10 through the suction port (not shown) is compressed and discharged from the discharge port 25 formed in the fixed spiral vane component 4 to the discharge valve 26.
Is pushed open to be discharged to the discharge cavity 27, and flows out through a discharge port (not shown).

A flat thrust bearing 28 is disposed on the end face of the rotation restraint component 24, and the thrust force generated by the pressure of the compressed gas in the compression working space 10 is applied to the swirl vane component 7 through the thrust bearing 28. It is supported on the back side of the swiveling end plate 8.

Next, a drive mechanism that makes the turning radius variable will be described. As shown in the exploded perspective view of FIG. 2, an eccentric hole 20 and a cylindrical concave portion 21 that opens to the spindle side in an area larger than the hole area inside the boss 11 of the swirling spiral blade component 7.
An eccentric bush 19 having a rotator is fitted rotatably via a slewing bearing 12, and a drive pin 15 is press-fitted and fixed in an eccentric hole 20 of the eccentric bush. This drive pin 15
However, it is rotatably fitted in and coupled to an eccentric drive hole 18 which is eccentrically provided by a turning radius, in a cylindrical portion 17 which fits in a recess 21 of an eccentric bush formed in the inner end portion of the main shaft 16 with a small clearance.

A turning balance weight 29 for generating a centrifugal force in a direction to reduce the dynamic unbalance of the turning parts is attached to a mounting plate 22 integrally formed at the end of the eccentric bush 19 on the main shaft side.

FIG. 3 is a diagram for explaining the operation of the eccentric bush. In this figure, the line connecting the axis Os34 of the main shaft 16 and the center Oc35 of the eccentric bush 19 is the second coordinate axis 37.
And the axis Oc35 is perpendicular to the second coordinate axis 37.
The line passing through is defined as the first coordinate axis 36, and the first coordinate axis 3
The intersection of 6 and the second coordinate axis 37 is defined as the origin of each coordinate axis, the second coordinate axis 37 is positive on the side opposite to the axis Os34 of the main axis 16 with respect to the first coordinate axis 36, and on the axis Os side. Is the negative region, and the first coordinate axis 36 is the second coordinate axis 37.
With respect to the rotation direction of the main shaft 16, the second coordinate axis 37
The region in which the region from negative to positive is the positive region and the opposite side is the negative region, and the quadrant in which the first coordinate axis 36 is positive and the second coordinate axis 37 is positive is the first quadrant 38 and the first coordinate axis 36. Is negative and second
The quadrant where the coordinate axis 37 is positive is the second quadrant 39, the first coordinate axis 3
The quadrant in which 6 is negative and the second coordinate axis 37 is negative is in the third quadrant 40,
A quadrant in which the first coordinate axis 36 is positive and the second coordinate axis 37 is negative is defined as a fourth quadrant 41. In this state, the distance between Os and Oc becomes the turning radius described above. In this coordinate system, the centers of the eccentric drive hole 18 and the eccentric hole 20 formed in the eccentric bush 19, that is, the center Od42 of the drive pin 15 are located in the second quadrant.

With such a configuration, the eccentric bush 19
Makes it possible to swing about the center Od42 of the drive pin 15 as a rotation center, and the center Oc35 of the eccentric bush 19 moves on an arc having the distance between Od and Oc as a radius with the drive pin center Od42 as the center. At this time, the rotation of the eccentric bush 19 due to the swing motion can be restricted between the concave portion 21 of the eccentric bush and the cylindrical portion 17 of the main shaft 16 which fits in this with a small gap. Determine the range. During operation, the fluid compression gas force (tangential gas force Ft, radial gas force Fr) and centrifugal force of the swirling component (centrifugal force Fs of swirling spiral vane component 7 and eccentric bush 19, centrifugal force Fc of balance weight 29). Is considered to act on the eccentric bush center Oc35 in the direction shown in FIG.

These acting forces act as the center Od42 of the drive pin.
Is converted into a moment that rotates the eccentric bush 19 around the eccentric bush 19, and the eccentric bush 19 swings around the center Od42 of the drive pin as the center of rotation as described above,
The distance from the axial center Os34 of the eccentric bushing to the eccentric bush center Oc35 is changed. This means that the turning radius is variable, and it can be understood from FIG. 3 that the rotational moment during operation causes the eccentric bush 19 to swing in the direction in which the turning radius increases. As a result, the swirling spiral blade 9 comes into contact with the side wall of the fixed spiral blade 6, and the compression work space 1
A good sealing property in the radial direction of 0 is obtained. If the contact load between the blades at this time is too small, the contact between the blades deteriorates and a gap is created, which causes gas leakage. On the contrary, if it is too large, it causes wear. When the angle formed by the first coordinate axis 36 and the line connecting Oc and Od is α as shown in FIG. 3,
The contact load Fw is determined from the balance between the gas force (Ft, Fr) and the centrifugal force (Fc, Fs) described above, and is given by the following equation.

Fw = Ft × tan α + Ft−Fr−Fc (1) Therefore, the weight amount of the turning balance weight 29 is adjusted so that the angle α is selected and the contact load does not become excessive during high speed operation. As a result, an appropriate sealing force is obtained while reducing the wear between the blades, and a smooth swirling motion of the swirling spiral blade component 7 is realized.

The axial gap that governs the amount of compressed gas leaking from the compression work space 10 is managed by adjusting the thickness of a shim (not shown) inserted between the front casing 2 and the rear casing 3, In addition, fixed spiral blade parts 4
The adjustment of the relative angle between the swirling spiral blade component 7 and the swirling spiral blade component 7 is performed by an angle adjusting rod (not shown) inserted from a hole (not shown) provided in the front casing 2.

Further, in order to suppress the vibration due to the dynamic unbalance of the compressor, a balance weight 32, which is provided on the main shaft 16 and generates a centrifugal force in the same direction as the turning balance weight 29, and an electromagnetic clutch 31, which are opposite to each other. The counter weights 31 that generate centrifugal force in the direction balance the generated moments of the compressor.

In terms of reliability, since the turning radius is variable when dust is generated, the swirling spiral blade 9 avoids damage by overcoming dust while reducing the turning radius. Further, the drive pin center Od42, that is,
The center of rotation of the swing of the eccentric bush 19 is the second quadrant 39.
The eccentric bush 1 is operated by the inertial force of the swiveling component when the acceleration is rapidly increased, such as at the time of starting.
Swing 9 away from each other to release the pressure in the compression work space 10 and cause abnormal noise or shock at the start.
It has the effect of alleviating liquid compression. This is one of the major features of the present invention, but if the reliability at the time of starting as described above is not taken into consideration, even if the position of the drive pin center Od42 is selected in the fourth quadrant 41, during operation, It can be easily estimated from the present invention that the contact load is automatically obtained at the line contact portions of both spiral blades.

Further, since the separate drive pin 15 is press-fitted and fixed to the eccentric bush 19, the workability is improved as compared with the conventional compressor, and the rotation regulation due to the swing of the eccentric bush 19 is eccentric. The recess 21 of the bush,
Since this is performed between the concave portion 21 and the cylindrical portion 17 of the main shaft that fits in a small gap, it is not necessary to provide a rotation angle range limiting means in a separate configuration as in the conventional case, and the structure is simplified. As a result, the manufacturing cost is reduced, and it is possible to provide an inexpensive scroll compressor.

Further, in the eccentric bush 19, a cylindrical concave portion 2 having an area larger than the hole area of the eccentric hole 20 and opening on the spindle side.
Since No. 1 is provided, the center of gravity of the eccentric bush 19 in the axial direction approaches the turning end plate 8. Therefore, even when the orbiting balance weight 29 is attached to the end surface of the eccentric bush 19 on the main shaft side, the center of gravity in the axial direction can be easily located near the center of the bearing surface of the orbiting bearing 12. As a result, tilting of the eccentric bush system during swivel motion can be suppressed, and the reliability of the swivel bearing 12 can be improved.

Next, an embodiment using the second technical means of the present invention will be described with reference to FIG.

According to the present invention, a turning radius variable drive mechanism using an eccentric bush similar to that of the above-mentioned embodiment is provided with an L-shaped step 43 on the outer peripheral end surface of the turning balance weight 29 on the main shaft side. The center of gravity of the turning balance weight 29 in the axial direction approaches the turning end plate 8. This makes it easier to position the axial center of gravity of the eccentric bush system including the swing balance weight 29 near the center of the bearing surface of the swivel bearing 12, and further to prevent the eccentric bush system from tilting during swiveling operation. It suppresses and further improves the reliability of the slewing bearing 12.

Next, an embodiment using the third technical means of the present invention will be described with reference to FIG.

The present invention relates to a turning radius variable drive mechanism using an eccentric bush similar to that of the above-described embodiment, and includes an eccentric bush 1.
A hole 44 is provided in the mounting plate 22 of the orbiting balance weight 29 integrally formed at the end of the rotating shaft 9 on the main shaft side to reduce the weight of the mounting plate 22 located outside the bearing surface of the orbiting bearing 12. As a result, the center of gravity of the eccentric bush system in the axial direction is more likely to be located near the center of the bearing surface of the slewing bearing 12, so tilting of the eccentric bush system during swivel motion is further suppressed, and the slewing bearing 12 The reliability of is improved.

Next, an embodiment using the fourth technical means of the present invention will be described with reference to the sectional view of the compressor shown in FIG.

According to the present invention, a through-hole 45 is provided inside the drive pin 15 in the swing radius variable drive mechanism using an eccentric bush similar to that of the above-mentioned embodiment, and a lubricating oil return path to the swing bearing 12 is constructed. are doing. As a result, oil or oil mist after lubricating the orbiting bearing 12 is returned to the internal space of the compressor housing 1 from the through hole 45 without being retained inside the boss 11 of the orbiting spiral blade component 7. Sufficient lubricating oil is secured to the slewing bearing 12, and the reliability of the slewing bearing 12 is enhanced.

Although the present invention has been described with reference to the embodiment of the scroll compressor for a vehicle in which the pressure is low inside the compressor housing, the present invention is not limited to such an embodiment. It goes without saying that various designs are possible within the scope of the present invention, such as a hermetic compressor having a built-in electric motor and a high-pressure type compressor in which the pressure inside the compressor housing is high.

[0047]

As is apparent from the above description, according to the present invention, the eccentric bushing swings around the center of the drive pin located in the second quadrant as the center of rotation by the action force of the fluid compression gas force and the centrifugal force. However, since the swirling radius is made variable, the swirling spiral blade comes into contact with the fixed spiral blade following to improve the radial sealing property of the compression work space. In addition, when the acceleration rapidly increases, such as at the time of starting, the inertial force of the swiveling component acts to swing the eccentric bush in the direction in which both blades separate, releasing the pressure in the compression work space, and causing abnormal noise at the time of starting. It has the effect of relieving abnormal shock and fluid compression.

Further, since the separate drive pin is press-fitted and fixed to the eccentric bush, compared with the conventional compressor,
The workability is improved, and the rotation cost due to the swing of the eccentric bush is controlled between the concave part of the eccentric bush and the cylindrical part of the main shaft that fits in this concave part with a small gap, so the manufacturing cost is reduced. Have the effect of

Further, since the eccentric bush is provided with a cylindrical recess having an area larger than the hole area of the eccentric hole and opening on the spindle side, the center of gravity of the eccentric bush in the axial direction approaches the swivel end plate, and the swivel balance is provided on the end face. Even with the weight attached, it is easy to position the center of gravity in the axial direction near the center of the bearing surface of the slewing bearing, and the tilting of the eccentric bush system during swivel movement is suppressed, and the reliability of the slewing bearing is improved. To be enhanced.

Further, according to the present invention, the outer peripheral end surface on the main shaft side of the turning balance weight is formed in an L-shaped step so that the center of gravity of the turning balance weight in the axial direction approaches the turning end plate, and this turning is performed. Since it is easier to position the center of gravity of the eccentric bush system including the balance weight in the vicinity of the center of the bearing surface of the slewing bearing, it is possible to further suppress the tilting of the eccentric bush system during the swivel operation, The reliability of the slewing bearing can be further improved.

Further, according to the present invention, the mounting plate of the orbiting balance weight integrally formed at the end of the eccentric bush on the main shaft side is provided with a through hole to reduce the weight of the mounting plate located outside the bearing surface of the orbiting bearing. Since the center of gravity of the eccentric bush system in the axial direction is located more easily near the center of the bearing surface of the slewing bearing, tilting of the eccentric bush system during swivel movement is further suppressed, and the reliability of the slewing bearing is improved. It can be increased.

Further, according to the present invention, the through hole provided inside the drive pin prevents the lubricating oil for the slewing bearing from being retained inside the boss of the swirl spiral vane component and through the through hole inside the compressor housing. Since the oil is returned to the space, sufficient lubricating oil is secured for the slewing bearing, and the reliability of the slewing bearing is enhanced.

[Brief description of drawings]

FIG. 1 is a sectional view of a scroll compressor showing an embodiment of the present invention using the first means.

FIG. 2 is an exploded perspective view of a drive mechanism using an eccentric bush.

FIG. 3 is an operation explanatory diagram of the eccentric bush.

FIG. 4 (a) is a plan view showing a state in which the turning balance weight according to the embodiment of the present invention using the second means is attached to an eccentric bush.

FIG. 5 is a plan view showing a state in which a turning balance weight is attached to the attachment plate of the eccentric bush of the embodiment of the present invention using the third means (b) The same sectional view

FIG. 6 is a sectional view of a scroll compressor showing an embodiment of the present invention using a fourth means.

FIG. 7 is a sectional view of a scroll compressor showing a conventional example.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Compressor housing 4 Fixed swirl vane component 5 Fixed end plate 6 Fixed swirl vane 7 Swirling swirl vane component 8 Swirling end plate 9 Swirling swirl vane 10 Compression working space 11 Boss 12 Slewing bearing 15 Drive pin 16 Main shaft 17 Cylindrical part of main shaft 18 Eccentric drive Hole 19 Eccentric bush 22 Flat plate 23 Rotation restraint part 29 Revolving balance weight 34 Main shaft axis Os 35 Center of eccentric bush Oc 36 First coordinate axis 37 Second coordinate axis 38 First quadrant 39 Second quadrant 40 Third quadrant 41 First 4 quadrants 42 Drive pin center Od 43 L-shaped step of turning balance weight 44 Drill hole 45 Through hole

Claims (4)

[Claims] 1. A fixed spiral vane component in which a fixed spiral vane is extended on a fixed mirror plate so as to form a plurality of compression working spaces in a compressor housing, and a swirl spiral vane is mounted on the swirl mirror plate. A swirling spiral blade part having a boss formed on the surface opposite to the extending surface of the swirling spiral blade is provided, and a drive mechanism for imparting a swirling motion to the swirling spiral blade part is provided with a boss of the swirling spiral blade part. A slewing bearing provided inside,
An eccentric bush that is rotatably supported in the boss through the swivel bearing, and has an eccentric hole and a cylindrical recess that opens toward the spindle with an area larger than the hole area; and a spindle side of the eccentric bush. The turning balance weight that reduces the dynamic unbalance of the turning parts attached to the mounting plate integrally formed at the end, the drive pin that is press-fitted and fixed in the eccentric hole of the eccentric bush, and the inner end of the eccentric bush. A cylindrical portion that fits in a small gap is formed in the concave portion, and a main shaft rotatably supported by the compressor housing and the drive pin eccentrically provided on the end surface of the cylindrical portion of the main shaft are rotatably fitted and joined. An eccentric drive hole and a rotation restraint component that restrains rotation of the swirling spiral blade component to rotate only, and a line connecting the axis of the main shaft and the center of the eccentric bush is defined as a second coordinate axis. Then, a line that passes through the center of the eccentric bush at a right angle to the second coordinate axis is defined as a first coordinate axis, and an intersection of the first coordinate axis and the second coordinate axis is defined as an origin of each coordinate axis, The second coordinate axis is positive with respect to the first coordinate axis on the side opposite to the axis of the main axis,
A region on the axial center side is a negative region, the first coordinate axis is a positive region in which the region of the second coordinate axis changes from negative to positive, in the order of the rotation direction of the main axis with respect to the second coordinate axis. The opposite side is a negative region, the first quadrant is a quadrant in which the first coordinate axis is positive and the second coordinate axis is positive, and the second quadrant is a quadrant in which the first coordinate axis is negative and the second coordinate axis is positive. The quadrant in which the first coordinate axis is negative and the second coordinate axis is negative is defined as a third quadrant, and the quadrant in which the first coordinate axis is positive and the second coordinate axis is negative is defined as a fourth quadrant. A scroll compressor in which the center of the eccentric hole of the eccentric bush, that is, the center of the drive pin is located in the second quadrant. 2. The scroll compressor according to claim 1, wherein an outer peripheral end surface portion of the orbiting balance weight on the main shaft side is formed with an L-shaped step. 3. The scroll compressor according to claim 1, wherein a hole is provided in a mounting plate of an orbiting balance weight integrally formed at an end of the eccentric bush on the main shaft side. 4. The scroll compressor according to claim 1, wherein a through hole is provided inside the drive pin.