JPH0327721B2 - - Google Patents

Description

[Detailed Description of the Invention] [Field of Industrial Application] The present invention relates to a fine adjustment mechanism for scroll fluid machines used in compressors such as air compressors and refrigerant compressors, pumps, expanders, etc. be.

[Conventional technology]

The principle of fluid machines, also known as scroll fluid machines, has been known for a long time, and applications have been considered for various applications such as compressors, pumps, and expanders. FIG. 25 shows the basic components of a scroll fluid machine. In the figure, 1 is a fixed scroll, 2 is an oscillating scroll, 1a is a discharge port, P is a compression chamber, and O is on a fixed scroll 1. The fixed point O' is a fixed point on the swinging scroll 2. The fixed scroll 1 and the oscillating scroll 2 each have spiral side plates 101 and 201 of the same shape and opposite winding directions formed integrally on a base plate (to be described later), and are combined with each other as shown in FIG. 25. The spiral side plates 101 and 201 are in contact with each other on their axial side surfaces. The shape of the spiral side plates 101, 201 is formed by an involute curve or the like, as is conventionally known.

Next, the operation when this scroll fluid machine operates as a compressor will be explained. In FIG. 25, the fixed scroll 1 is stationary with respect to space, and the swinging scroll 2 is combined with the fixed scroll 1 as shown in the figure, and performs rotational movement without changing its attitude with respect to space. , Figure 1
Move like 0°, 90°, 180°, 270°. As the oscillating scroll 2 moves, each point B moves toward the center, and the three-way compression chamber P formed between the fixed scroll volute side plate 101 and the oscillating scroll volute side plate 201 gradually reduces its volume. This compression chamber P
The gas taken in is compressed and discharged from the discharge port 1a. During this time, the distance from O to O' in FIG. 25 is kept constant, and if the distance between the spiral side plates 101 and 201 is expressed by Z and the thickness is expressed by t, then OO'= ^Z ₂ -t. Z corresponds to the pitch of the spiral side plates 101 and 201. In addition, in FIG. 25, the oscillating scroll 2 is rotated in the opposite direction, that is, 0°, 270°, 180°,
Needless to say, if you rotate it 90 degrees, it will work as an expander.

The specific structure of a scroll fluid machine that operates according to such an operating principle will be explained with reference to FIG. 26. FIG. 26 shows one conventional example in which a scroll fluid machine is applied as a compressor. In the figure, 1 is a fixed scroll, 2 is an oscillating scroll, 1a
is a discharge port, P is a compressor, 1b is a suction port, 3 is a main shaft, and 4 is a frame. Further, 101 and 201 are spiral side plates of the fixed scroll 1 and the swinging scroll 2, respectively, and 102 and 202 are base plates of the fixed scroll 1 and the swinging scroll 2, respectively. In addition, A is the end surface 1 of the spiral side plates 101, 201.
01a, 201a, and the bottom surfaces 202a, 102 of the mating base plates 202, 102 that come into contact with these, respectively.
It is the axial distance between a and a.

Here, the oscillating scroll 2 has a frame 4 on the opposite side of the base plate 202 to the side on which the spiral side plate 201 is formed.
The fixed scroll 1 is combined with the fixed scroll 1 in the state shown in FIG. 25 while being supported by the fixed scroll 1, and the fixed scroll 1 is fixed to the frame 4. When the main shaft 3 rotates in the direction of the arrow, the swinging scroll 2 connected thereto begins to move. Here, the oscillating scroll 2
performs revolving motion without rotating on its own axis by means of an anti-rotation device (not shown). As a result, the fluid to be compressed is sucked through the suction port 1b, compressed according to the operating principle shown in FIG. 25, and discharged from the discharge port 1a.

In such a fluid machine, leakage in the radial direction of the spiral through the radial seal, that is, the gap A, is relative to the fluid intake volume because the leakage line length corresponds to the longitudinal length of the spiral. This has a large impact on machine efficiency. As a method of sealing in this radial direction, the distance A is made very small, for example, as shown in Japanese Patent Application Laid-Open No. 55-46081,
It is possible to prevent leakage of the compressed fluid by sucking oil together with the compressed fluid from the suction port 1b and forming an oil film in the small gap A, but in order to uniformly provide such a small gap, High dimensional accuracy is required for each part such as the fixed scroll 1, the oscillating scroll 2, and the frame 4, and in some cases, it may be necessary to selectively fit each part during assembly, which poses problems in workability and assembly. Ta. Further, during operation, the vicinity of the discharge port 1a becomes high in temperature due to the compressed fluid, and as a result, if the local thermal expansion exceeds the minute distance A, seizure occurs because there is no escape. Therefore, it is necessary to assume the amount of thermal expansion and make the distance uniformly large over the entire A side in advance, but if you do this, the distance will be greater than the optimum distance required to form an effective oil film. As a result, leakage was large and the seal was often ineffective.

On the other hand, in addition to these non-contact seals, a groove is formed along the longitudinal direction of the spiral on the end surface of the spiral side plates 101, 201, and a sealing material is fitted into this groove to prevent leakage by a contact seal. A method is being considered.

Such a sealing method was originally disclosed in US Pat. No. 801,182 of 1905, and more recently, it is disclosed in Japanese Patent Application Laid-Open No. 117304/1984.

As an example, the one shown in Japanese Patent Application Laid-Open No. 117304/1983 will be explained with reference to FIGS. 27 to 29. That is, FIG. 27 shows the bottom surface 102a of one fixed scroll plate.
It is a partial cross-sectional view of the vicinity of part A between the spiral side end face 201a of the oscillating scroll 2, and the spiral side plate 201.
A groove 5 having a rectangular cross section and opening along the spiral longitudinal direction of the end face 201a is formed, and a sealing material 51 having the same shape as the groove 5 is fitted into the groove 5. Here, there is a gap 501 between the side surface 5b of the groove 5 and the side surface 51b of the sealing material 51 along the longitudinal direction of the spiral, and a bottom surface 5d of the groove 5.
The dimensions of the groove 5 and the sealing material 51 are determined so that a gap 502 is provided between the bottom surface 51d of the spiral side plate 201 and the bottom surface 51d of the spiral side plate 201, and as a result, the end surface 201a of the spiral side plate 201 and the base plate Bottom 1
Even if there is a gap A between 02a, the spiral side plate 20
The seal between the high-pressure side compressor P _H and _the low-pressure side compression chamber P _L , which are partitioned by As a result, a force is applied as shown by arrow F, so that the sealing material 51 is applied to the base plate bottom surface 10.
The upper surface 51a and side surface 51c of the sealing material 51 are pressed against the groove 5 side surface 5c and the upper surface 51a of the sealing material 51, respectively, and the sealing material 51 is brought into close contact with the base plate bottom surface 102a and the groove side surface 5c, thereby preventing gas leakage.

In such a sealing method, it is possible to effectively seal against leakage in the radial direction of the spiral through the gap A between the end surface of the spiral side plate and the end surface of the base plate, but the leakage in the spiral radial direction can be effectively sealed by the spiral side plates 101 and 201. Between each compressor P partitioned by B, there are 501 and 502
It has the disadvantage that it tends to leak in the longitudinal direction through the spiral.

That is, FIG. 28 shows the spiral side plates 101, 201.
Partial cross-sectional view of the vicinity of contact point B seen from above, No. 29
The figure is also a partial cross-sectional perspective view, but as shown by the solid arrow from the high pressure side compressor P _H , gas passes through gaps 501 and 502 to the downstream low pressure side compressor.
This shows a state where it is leaking to P _L. As described above, this type of sealing method effectively performs sealing in the radial direction, but as a means for doing so, the groove 5 and the sealing material 5 are
Since gaps 501 and 502 must be provided between the two, as a result, leakage in the longitudinal direction of the spiral inevitably occurs, and compression efficiency, that is, performance inevitably deteriorates. Especially depending on the machining accuracy, the distance between 501 and 5
02 has the possibility of causing an increase in leakage passing through the gaps 501 and 502 or an increase in leakage in the radial direction due to a decrease in the followability of the sealing material 51 itself.

Furthermore, since the upper surface 51a of the sealing material 51 slides while being pressed against the base plate bottom surface 102a by the gas, the sliding loss and wear of this portion cannot be ignored.

In addition, as a means to prevent such leakage in the longitudinal direction of the spiral, for example, in Utility Model Application No. 57-180182, as shown in FIG. This problem is attempted to be solved by making the thickness dimension H of the sealing material 51 larger than the depth dimension H' of the groove 5, while making them substantially the same.
However, in this method, it is difficult to control the dimensions of H and H', and if H-H'>A, there will be a gap in the axial direction, which will cause leakage in the radial direction. If H'<A, the sealing material 51 is fixed scroll 1 and oscillating scroll 2.
It becomes wedged in shape, making it impossible to obtain smooth rotational drive.

[Problem that the invention seeks to solve]

As mentioned above, in conventional scroll fluid machines,
In the non-contact sealing method, in order to make the distance in the axial direction uniform and small, there are problems in precision control such as machining accuracy, and if the distance is narrowed, the tips of the spiral teeth may expand due to thermal expansion during operation. There was a problem with reliability, such as contact between the two, causing seizure, and a contradictory problem in that performance deteriorated if a gap was left in order to prevent this. Furthermore, in the contact sealing method, when a gap is provided between the sealing material and the groove and the sealing is performed by gas pressure or the like, problems arise such as performance degradation due to leakage from the gap and wear of the sealing material.
Furthermore, when sealing is performed using a sealing material without providing a gap between the sealing material and the groove, there are problems such as strict accuracy control being required, similar to the non-contact sealing method.

The present invention has been made to solve these problems, and has a simple structure, is easy to assemble, has high workability, can tolerate thermal deformation during operation, and is effective in preventing leakage during operation. The purpose of the present invention is to provide a mechanism for finely adjusting the assembly of a scroll fluid machine that is highly efficient and highly reliable.

[Means for solving problems]

The scroll fluid machine according to the present invention combines a fixed scroll and an oscillating scroll, each of which has a spiral side plate such as an involute protruding from the base plate surface, with each other. In a scroll fluid machine configured to form a chamber and rotate an oscillating scroll to transfer, compress or expand the fluid taken into the chamber, a scroll having the same shape as each scroll side plate of both scrolls is provided. A pair of fine adjustment elements having a shape and a guide portion for press-fitting the same in the direction of the spiral axis are provided on the end faces of the spiral side plates of both scrolls, and each of the fine adjustment elements is provided in each of the corresponding guide portions. The fine adjustment element moves in the direction of the spiral axis during press-fitting so that the distance between the end face of each of the spiral side plates and the bottom of the corresponding base plate can be finely adjusted via the fine adjustment elements. A fine adjustment mechanism is provided in which a hollow part is provided in the axial direction between the guide part and the hollow part, and this hollow part is communicated with the spiral side plate or the end face side of the fine adjustment element at a plurality of locations. .

[Effect]

As described above, by press-fitting the fine adjustment elements evenly into the guide portions provided on the end faces of the spiral side plates of the scroll, each spiral side plate of the fixed scroll and the oscillating scroll can be inserted through the fine adjustment elements. It is possible to perform fine adjustment of the axial distance between the end face and the end face of the base plate, eliminating variations in machining accuracy of fixed scrolls, oscillating scrolls, etc., and making virtually no gaps or the necessary minimum minute gaps. This space can be adjusted by providing a space in the axial direction between the fine adjustment element and the guide part.
Since the part and the end face side of the spiral side plate or fine adjustment element are electrically connected at multiple points, the pressure between the hollow part and the chamber is almost equalized, making it easy to make fine adjustments due to fluctuations in chamber pressure during operation. The element can be prevented from moving in the axial direction, so no force is generated in the fine adjustment element in the axial direction, there is no frictional resistance or wear between the element and the base plate, and the element does not sink into the guide section. This provides a highly reliable fine adjustment mechanism that is fixed in a stable state without any leakage and has little leakage.

[Embodiments of the invention]

An embodiment of the present invention will be described below with reference to FIGS. 1 to 18. FIG. 1 shows a specific example in which a scroll compressor is applied to a totally hermetic refrigerant compressor.

In the figure, 1 is a fixed scroll, 2 is an oscillating scroll, 1a is a discharge port bored in the center of the fixed scroll 1, and 1b is a peripheral wall 10 of the fixed scroll 1.
The suction port formed at 3, P is a compressor. Each fixed scroll 1 is composed of a disc-shaped base plate 102 and a spiral side plate 101 integrally formed with this base plate 102, and the oscillating scroll 2 is similarly formed integrally with a disc-shaped base plate 202. The scrolls 1 and 2 are interlocked with each other to form a base plate 102, 202 and a spiral side plate 10.
A compressor P is formed surrounded by 1 and 201. A plurality of compressors P are formed, and a central pressure chamber having the highest pressure among them is configured to communicate with the discharge port 1a.

Each end surface 101 of the spiral side plates 101, 201
a, 201a, along the longitudinal direction of the spiral, leaving an inner end and an outer end in the spiral direction,
Grooves 5 serving as guide portions are formed in each of them, and fine adjustment elements 6 are fitted into each of these grooves 5, respectively. This element 6 is guided by the groove 5 and press-fitted into the groove 5 so that both sides of the element 6 are in complete contact with each other in the longitudinal direction of the spiral.

Further, 3 is the main shaft, and 301 is the spiral side plate 101, 2.
An eccentric bushing 40 that applies a pressing force to the oscillating scroll 2 so that the side surfaces of the side plates 101 and 201 are always in contact with each other at the B portion even if 01 is worn out has an outer peripheral surface shape that is almost the same as that of the fixed scroll 1; Moreover, the upper frame 41 has the same maximum outer diameter as the orbiting scroll 1, and the outer peripheral surface shape is almost the same as that of the fixed scroll 1, and the maximum outer diameter is the upper frame 4.
0, a lower frame larger than 0, 401 an Oldham joint, 402 an annular upper thrust bearing that receives the pressure of the compression chamber P and the own weight of the oscillating scroll 2, 41
1 is an annular lower thrust bearing that receives the weight of the main shaft 3 and other thrust loads applied to the main shaft 3, and 703 is an upper main bearing that receives the radial load of the main shaft 3 at its upper part. In this embodiment, a metal bearing is used. . 412 is a lower main bearing that receives the radial load of the main shaft 3 at its intermediate portion, and in this embodiment, a bearing metal is used.

Back surface 202b of base plate 202 of swinging scroll 2
At the center is a shaft 203 whose axis is perpendicular to the back surface 202b of the base plate 202 and parallel to the axis of the main shaft 3.
is integrally formed, and an eccentric hole 3a having an axis parallel to the axis (rotation center) of the main shaft 3 is formed on the upper end surface of the main shaft 3. A bushing 301 is fitted. This eccentric bush 301 is eccentric with respect to its outer periphery, and an eccentric hole 30 whose axis is parallel to the axis of the main shaft 3
1a, and the shaft 203 is rotatably fitted into this eccentric hole 301a.

The main shaft 3 is supported by an upper main bearing 403 disposed on an upper frame 40 and a lower thrust bearing 411 and a lower main bearing 412 disposed on a lower frame 41. The upper main bearing 403 and the lower main bearing 412 are assembled concentrically with each other by a solder fitting part or the like. Further, the upper main bearing 403 and the upper thrust bearing 402 are concentric, and the axis of the upper main bearing 403 and the bearing surface 402a of the upper thrust bearing 402 are perpendicular, so that the axis of the main shaft 3 is the same as that of the upper thrust bearing 402. It is concentric with the axis of the upper thrust bearing 402, and the bearing surface 4 of the upper thrust bearing 402
02a. Moreover, since the rocking scroll 2 is supported by the bearing surface 402a of the upper thrust bearing 402 on the back surface 202b of the bed plate 202, the rocking scroll 2 is
02 is maintained perpendicular to the main axis 3.

The Oldham joint 401 is a joint means for preventing the rotation of the rocking scroll 2 and allowing the rocking scroll 2 to perform only revolving motion around the axis of the main shaft 3. 202 and
It is arranged between the upper frame 40 and the upper frame 40 .

After the above-mentioned mechanical parts are assembled in the above-mentioned relative relationship, each fine adjustment element 6 in each groove 5 of the fixed scroll 1 and the swinging scroll 2 is installed in a state in which it protrudes more than each groove 5, and is attached to the upper frame. 40, the lower frame 41 and the fixed scroll 1 are fastened together by a plurality of bolts 42 that pass through the peripheral wall 103 of the fixed scroll 1 and the upper frame 40, and the threaded portion 42a at the tip is screwed only into the lower frame 41. be done. This state is shown in FIG. Here, the fixed scroll 1 has a lower surface 1 of the peripheral wall portion 103.
03a, the upper thrust bearing 40 is fixed to the mounting surface 40a formed on the upper surface of the outer peripheral part of the upper frame 40.
The back surface 202b of the base plate 202 of the orbiting scroll 2, the bottom surface 202a that is the opposite surface, and the end surface 201a of the spiral side plate 201 are parallel to each other, and the fixed scroll The lower surface 103a of the peripheral wall of the fixed scroll 1 and the end surface 101a of the spiral side plate 101 are on the same plane, and the end surface 101a and the bottom surface 102a of the base plate 102 are parallel.
01a and the base plate bottom surface 202a of the rocking scroll 2, and between the spiral side plate end surface 201a of the rocking scroll 2 and the base plate bottom surface 102a of the fixed scroll 1 are maintained parallel to each other. Therefore, each element 6 is connected to the base plate bottom surface 1 of the fixed scroll 1, respectively.
02a, it is pressed by the base plate bottom surface 202a of the orbiting scroll 2 and is uniformly press-fitted into the groove 5.
Then, the fixed scroll 1 is fixed to the frame 4.
0 to the frame 41 with the bolts 42, the spiral side plate end face 101a of the fixed scroll 1, the base plate bottom face 202a of the swinging scroll 2, the spiral side plate end face 201a of the swinging scroll 2, and the fixed scroll 1 Base plate bottom surface 102a
Since a slight gap A is uniformly formed between them, each element 6 is pushed into each groove 5 until it protrudes uniformly from each groove 5 by this minute gap A, and then stops. . As a result, each spiral side end face 101a, 201a and the bottom face 2 of the opposite base plate
There is virtually no space between 02a and 102a via the above-mentioned elements 6.

Next, in FIG. 1, to support the motor that rotates the main shaft 3, the rotor 70 of the motor is fixed to the main shaft 3 by shrink fitting, etc., and the motor is rotated while adjusting the rotor 70 to ensure an appropriate air gap. A stator 71 is fixed to the lower frame 41 with bolts or the like.

Mechanical parts 8 in which the above-mentioned respective mechanical parts are assembled in the above-mentioned relative relationship, that is, fixed scroll 1, swinging scroll 2, upper frame 40, and lower frame 4
1. The main shaft 3, rotor 70, stator 71, and other assemblies are housed in a shell 9, which is a closed container. Here, the shell 9 is divided into three parts: an upper lid 901, an intermediate cylindrical part 902, and a bottom lid 903.
is fixed to the intermediate cylindrical portion 902 at the outer periphery of the lower frame 41 by shrink fitting or spot welding, and the upper lid 901 and the bottom lid 903 are attached to the outer periphery of the intermediate cylindrical portion 902 at both ends of the intermediate cylindrical portion 902 as shown in the figure. are fitted together so as to cover them,
These fitting parts are sealed by welding. 904
is a suction pipe 9 which is connected to the peripheral wall of the intermediate cylindrical portion of the shell by welding or the like and opens into the internal space 9a of the shell 9;
05 is a discharge pipe that passes through the center of the shell upper lid 901, is airtightly connected to this center, and is further extended to communicate with the discharge port 1a of the fixed scroll 1, and 906 is welded to the shell upper lid 901. , the motor stator 71 is connected to the motor stator 71 by a lead wire (not shown).
A sealed terminal 907 is electrically connected to lubricating oil stored at the bottom of the shell 9. Here, the lower end of the main shaft 3 is immersed in lubricating oil 907. Further, the joint between the discharge pipe 905 and the discharge port 1a is sealed with an O-ring or the like.

The main shaft 3 is formed with an eccentric oil supply hole 3b that penetrates from the lower end of the main shaft 3 to the eccentric hole 3a formed at the upper end, so that various parts of the bearing are supplied with oil.

The operation of the scroll compressor configured in this way will be explained next. When the motor stator 71 is energized through the sealed terminal 906, the motor rotor 70
generates torque and rotates together with the main shaft 3. When the main shaft 3 starts rotating, the rotational force of the main shaft 3 is transmitted to the shaft 203 of the swinging scroll 2 through the eccentric bush 301 fitted into the eccentric hole 3a of the main shaft 3, and the swinging scroll 2 is connected to the Oldham joint 401. The main shaft 3 rotates around the axis of the main shaft 3 without rotating, and the above-described compression action shown in FIG. 25 is performed in the compression chamber P.

At this time, the end surface 101 of the spiral side plates 101, 201
a, 201a, and a base plate 202 facing these,
The element 6 is fitted into the groove 5 so as to fill the minute gap A between the bottom surfaces 202a and 102a of 102.
substantially in the direction of the base plate bottom surfaces 202a, 102a, and the end surfaces 101a, 201a are uniformly moved without any gaps.
Since it protrudes more, it prevents compressed refrigerant gas from leaking through the minute gap A in the spiral radial direction, that is, from the relatively high-pressure compression chamber to the low-pressure compression chamber. Furthermore, the side surfaces of the spiral side plates 101 and 201 swing the eccentric bushing 301 around the shaft 203 of the swinging scroll 2 by using centrifugal force generated by the eccentric rotation of the swinging scroll 2. , by making the amount of eccentricity of the oscillating scroll 2 variable with respect to the axis of the main shaft 3, the spiral side plate 1 is
01 and 201 are brought into contact with each other at part B, and leakage of the compressed refrigerant from the relatively high-pressure compression chamber to the low-pressure compression chamber occurs in the spiral direction through the side surfaces of the spiral side plates 101 and 201. Prevented. In this way, leakage during compression is largely prevented,
This enables operation with high compression efficiency.

Next, the flow of refrigerant gas will be explained. The suction refrigerant gas from the evaporator (not shown) is supplied to the suction pipe 904.
It flows into the shell inner space 9a and cools the motor rotor 70, motor stator 71, etc., and
It passes through a suction passage provided on the outer periphery of the lower frame 41 (not shown), is sucked in through the suction port 1b, is taken into the compression chamber P, is compressed, becomes high-pressure refrigerant gas, and is discharged through the discharge port 1b. The water is discharged from the shell 9 through a pipe 905 to a condenser (not shown).

Next, the oil supply system will be explained. The lubricating oil 907 stored in the lower part of the shell 9 is supplied to the eccentric oil supply hole 3b by the centrifugal pump action generated by the rotation of the main shaft 3.
The oil is pumped up through the eccentric hole 3a and supplied to the eccentric bush 301. Upper thrust bearing 402, lower thrust bearing 411, upper main bearing 403, lower main bearing 41
2. Furthermore, after lubricating the Oldham joint 401, a portion is sucked into the compression chamber P together with the suction refrigerant gas, and is used for sealing and lubricating the compression part, and is then fed to the discharge pipe 9.
05, condenser, evaporator (not shown)
The oil returns to the shell 9 from the suction pipe 904, but most of the oil returns to the oil return holes 40b and 4 provided in the upper frame 40 and lower frame 41, respectively.
1a, it flows down and returns to the lower part of the shell 9.

FIG. 3 is a diagram showing in detail the configuration of the eccentric bush 301 inserted into the eccentric hole 3a of the main shaft 3, in which a is a top view, b is a side sectional view, and c is a bottom view.

301b is the outer peripheral surface of the eccentric bushing, and O _Bp is the center thereof. 301a is the inner circumferential surface of the eccentric bushing, and O _Bi is its center. Center O _Bi is the center
It is eccentric by ε with respect to O _Bp .

Reference numeral 301c denotes a vertically extending oil groove whose lower end is open to the lower end surface of the eccentric bushing and whose upper end is closed so as not to open to the upper end surface of the eccentric bushing, and is connected to the inner circumferential surface 301a. There is. 30
1d is an oil hole for communicating the oil groove 301c and the outer peripheral surface portion 301d, and 301e is the outer peripheral surface portion 3.
The oil hole 30 is located at the notch provided in 01b.
The radially outer end of 1d opens into this notch. Reference numeral 301f denotes a rotation stopper hole drilled in the lower end surface of the eccentric bushing 301 in the thick portion thereof. The eccentric bush 301 is made of a bearing material such as aluminum alloy or lead bronze.

FIG. 4 is a perspective view for explaining the assembly sequence when attaching such an eccentric bush 301 to the main shaft 3. In FIG. 4, first, a spring pin 32 having a substantially cylindrical shape with a C-shaped planar shape is fitted into the pin hole 31 at the bottom of the eccentric hole 3a of the main shaft 3.
The eccentric bush 301 is inserted into the eccentric hole 3a so that the rotation stopper hole 301f at the bottom of the eccentric bush 301 is aligned with the spring pin 32. With the spring pin 32 fitted into the rotation stopper hole 301f and the lower end surface of the eccentric bush 301 in contact with the bottom surface of the eccentric hole 3a, insert the snap spring 33 into the eccentric hole 3.
Snap spring groove 3 formed in the circumferential direction on the side a
Fit it into 4. The snap ring 33 is formed from a thin elastic wire such as piano wire into a C shape.

FIG. 5 is a diagram showing a state in which the eccentric bush 301 is assembled into the main shaft 3, and in this FIG.
O _S is the axis of the main shaft 3, that is, the rotation center, and this center O _S
The center O _Bp is located at a position where a straight line connecting O _Bi and the center O _Bi of the inner circumferential surface 301a of the eccentric bushing and a straight line connecting the center O Bi and the center of the outer circumferential surface 301b of the eccentric bushing make a substantially right angle. The position of the spring pin 32 has been determined. The diameter of the rotation stopper hole 301f is set larger than the diameter of the spring pin 32, so that the eccentric bush 301 can move in the circumferential direction to some extent. Further, the notch 301a is provided in the circumferential direction so that the oil hole 301d of the eccentric bush 301 and the oil hole 3c drilled in the radial direction of the large diameter part of the main shaft 3 are always in communication even when the eccentric bush 301 rotates. A predetermined length is formed. The oil pressure 3c further communicates with an oil groove 3d provided in the axial direction of the outer peripheral surface of the large diameter portion of the main shaft 3.

The oscillating shaft 203 of the oscillating scroll 2 is arranged in an eccentric bushing 301 so that the outer circumferential surface of the oscillating shaft 203 is connected to the inner circumferential surface 30.
1a, so that the center O _Bi of the inner circumferential surface 301a of the eccentric bush coincides with the center of oscillation, that is, the center of gravity of the oscillating scroll 2. Therefore, when the main shaft 3 rotates in the direction of the arrow W, a centrifugal force is generated in the direction of the arrow G on a straight line connecting the rotation center O _S of the main shaft 3 and the center O _Bi of the inner peripheral surface 301a of the eccentric bushing, and the centrifugal force is generated in the direction of the arrow G. 301, a moment is generated in the direction of arrow M around the center O _Bp of the outer circumferential surface 301b of the eccentric bush. Therefore, if there is a gap between the spiral side plates 101 and 201 of the fixed scroll 1 and the oscillating scroll 2, the eccentric bush 301 is moved so that the oscillating scroll 2 moves until the side plates 101 and 201 touch each other.
rotates in the direction of arrow M about the center O _Bp of the outer circumferential surface 301b of the eccentric bush.

The change in the center position will be explained with reference to FIG.
That is, the center of the eccentric bush outer peripheral surface 301b
The eccentric bushing 301 rotates in the direction of arrow M with O _Bp as the center, and the center of the eccentric bushing inner peripheral surface 301a
O _Bi is the point where the spiral side plates 101 and 201 touch each other
Move to O _Bi ′. That is, the revolution radius of the swinging scroll 2 changes from O _S O _Bi = R to O _S O _Bi ′=R′. Conversely, if the revolution radius is smaller than R due to machining accuracy, the eccentric bush rotates in the direction opposite to arrow M. This includes the liquid bag, both spiral side plates 101,
This also occurs when a transfer occurs between 201 and 201.

In this way, the eccentric bushing 5 absorbs variations in machining accuracy, facilitates assembly, and improves compression efficiency by preventing compressed refrigerant gas from leaking in the spiral direction between the spiral side plates 101 and 201 during compression. Furthermore, it is resistant to liquid baggage and foreign matter, and is useful for improving reliability.

Next, a detailed and specific explanation of the present invention will be given.
FIG. 7 shows that the element 6 is connected to an oscillating scroll 2.
FIG. 3 is a perspective view of the spiral side plate 201 when assembled, showing a state in which the spiral side plate 201 is press-fitted into a groove 5 formed along the longitudinal direction of the spiral. Groove 5 is the spiral side plate 2
01, and is formed along the longitudinal direction of the spiral leaving an inner end 201b and an outer end 201c in the spiral direction, and a string-like element 6 is attached to the opening surface of the groove 5 so as to fill the groove 5. Press down vertically. Here, an example of the swinging scroll 2 is shown, but it goes without saying that the fixed scroll 1 can also be implemented in the same manner. Below is the swinging scroll 2
I will only explain.

FIG. 8 is a local cross-sectional view in such a state, and the groove 5 and element 6 have a rectangular cross-section here. Here element 6
The width D of the element 6 is substantially equal to or larger than the width D' of the groove, and the thickness H of the element 6 is substantially the same as or smaller than the depth H' of the groove 5. It has become a value. When D>D', the element 6 must be made of a material that is easily deformed elastically or plastically in the width direction, and therefore, the element 6 used is a material having such properties. Polytetrafluoroethylene resin (PTFE), which has a certain degree of elastic-plastic flexibility and self-lubricating properties, is optimal. Also suitable are soft metals such as lead and solder that are easily plastically deformed, and materials made by combining PTFE with materials with high elasticity such as rubber.

FIG. 9 is a partial sectional view showing a state in which such an element 6 is inserted into the groove 5. The element 6 is elastically deformed (or may be plastically deformed) so that both side surfaces 6b and 6c are formed on both sides of the groove 5. a state in which it is in close contact with surfaces 5b and 5c and protrudes from the end surface 201a of the spiral side plate;
Therefore, the lower surface 6d of the element 6 and the bottom surface 5 of the groove 5
It remains in a state where there is an empty space 501 between d.
The axial dimension of this void 502 is assumed to be δ.

FIG. 10 shows such an oscillating scroll 2,
FIG. 3 is a partial cross-sectional view showing a state in which a fixed scroll is covered and fixed using the assembly method described in FIG. 2; The element 6 that protrudes from the above-mentioned spiral side plate end surface 201a by the base plate bottom surface 102a of the fixed scroll 1 is pushed downward into the groove 5 as shown by the arrow, and is connected to the base plate bottom surface 102a and the spiral side plate end surface 2.
It stops when it is pushed in to a position where the set minute distance A described above in FIG. 1 is created during 01a. At this time, it goes without saying that the axial dimension δ' of the space 501 satisfies δ'<δ. Here, the above-mentioned dimension δ' is determined by the fact that when the compressor is in operation, the temperature becomes high especially on the spiral center side, so the center side plate locally expands in the axial direction due to thermal expansion, and the dimension of the small distance A locally shrinks. Even if the element 6 is locally pressed down by the bottom surface of the mating base plate, the element 6 is further pushed and moved axially downward into the groove 5 by the bottom surface of the mating base plate, and due to this thermal expansion. It is set as a relief part to absorb dimensional changes.

If an elastic force acts on the element 6 in the axial direction, and therefore the upper surface 6a of the element 6 is pressed excessively against the bottom surface 102a of the base plate in the state shown in FIG. 10, as shown in FIG. Then, return the base plate 102 in the direction of the arrow to create a predetermined minute gap between the top surface 6a of the element 6 and the bottom surface 102a of the base plate.
All you have to do is offset it so that there is a gap A′.

One method of the above offset is shown in FIG. That is, after assembling by the assembly method explained in FIG. 6, the bolts 42 are removed and the fixed scroll 1 is removed from the upper frame 40 and the fixed scroll 1 peripheral wall bottom surface 103a and the mounting surface 4 of the upper frame 40
By inserting an annular shim with a uniform thickness and dimensions A' between 0a and 0a, tighten the bolt 42 again to separate each element of the fixed scroll 1 and the oscillating scroll 2 by the thickness of the shim A'. 6's top surface 6a and the corresponding base plate bottom surface 202a, 1
A minute gap A' is uniformly formed between 02a and 02a.

Another example of such an offset assembly method will be explained with reference to FIG. Swirl side plates 101, 20 of fixed scroll 1 and swinging scroll 2
The grooves 5 of the first end surfaces 101a and 201a are made to protrude in advance by a predetermined distance A of the element 6 or more. In this state, the upper frame 40
A solid flat surface 12a so that its lower surface 40b fits
The bearing surface 4 of the upper thrust bearing 402 is placed on the stand 12 having a
02a, an annular shim 10 having a uniform thickness and dimensions A' and having an inner and outer diameter that is approximately the same as that of the upper thrust bearing 402 is placed on top of the shim 10. , the shim 10 is placed on the thrust bearing 402 so as to be sandwiched therebetween. In this way, the spiral side plate 201 of the oscillating scroll 2 and the fixed scroll 1
The fixed scroll 1 is covered with the spiral side plates 101 of the scrolls 101 and 101 interlocking with each other. Next, in this state, the base 1 is pressed by the press arm 13 via the upper surface 102b of the fixed scroll 1 and the flat plate 11.
2. It is pressed perpendicularly to the plane 12a of No. 2. As a result, each element 6 of the fixed scroll 1 and the oscillating scroll 2 has a thickness A' of the shim 10 subtracted from the predetermined distance A press-fitted into the respective groove 5 by the base plate bottom surface 202a, 102a of the other. It stops in a state where it protrudes uniformly from each groove 5 by the dimension A''. After that, the shim 10 is removed and it is reassembled by the assembly method explained in FIG. There is a small amount uniformly between the plate bottom surfaces 102a and 202a.
A gap A′ can be formed.

In assembly as described above, by providing an axial fine adjustment mechanism consisting of an adjusting element 6 and a groove 5 into which it is inserted on the end face of the scroll side plate of each scroll, the end face of each scroll side plate and the bottom of the base plate corresponding thereto can be adjusted. The gap between the refrigerant and the refrigerant in the radial direction of the spiral during compression can be easily set through the element 6 with virtually no gap or with the minimum required gap that eliminates variations in machining accuracy. Can prevent gas leaks. Further, the side surfaces 6b, 6 where the element 6 and the groove 5 are in contact with each other
c, 5b, and 5c have virtually no gaps, so no leakage to the downstream side of the swirl occurs through these portions.

Furthermore, since the element 6 is fixed in the groove 5 by press-fitting or the like, essentially the upper surface 6a of the element 6 does not press against the bottom surface of the base plate, and therefore, during normal operation, the element 6
No wear occurs on the upper surface 6a. Furthermore, the fact that the pressing force is not generated on the bottom surface of the base plate means that there is no frictional resistance here, and therefore the eccentric bushing 301
can be operated smoothly. That is, due to the swing motion of the eccentric bush 301, the axis of the swing scroll 2 fitted therein moves relative to the axis of the main shaft 3. This oscillating motion is caused by the centrifugal force of the oscillating scroll 2 itself. However, when an excessive force is applied to the end surfaces 101a and 201a of the spiral side plates of the fixed scroll 1 and the orbiting scroll 2, the frictional resistance of these parts as well as the upper thrust bearing 402 that supports the force in the thrust direction of the orbiting scroll 2 are also affected. As a result, the frictional resistance of these sliding parts is
As the eccentric bushing 301 swings due to the above-mentioned centrifugal force, the side surface of the spiral side plate 201 of the oscillating scroll 2 changes to the spiral side plate 10 of the fixed scroll 1.
This acts to prevent the oscillating scroll 2 from moving in the direction in which it is pressed against the side of the side plate 1, preventing proper contact between the side plates, increasing leakage from these parts, and causing performance deterioration. If the load further increases, the upper thrust bearing 402 and the like will seize.

In the present invention, as described above, since the upper surface 6a of the element 6 is essentially not pressed against the bottom surfaces 102, 202a of each part of the base plate, the upper thrust bearing 4
No load is applied to the eccentric bush 3.
01 can be performed smoothly, and the side surfaces of the spiral side plates 101 and 201 can be effectively sealed accordingly.

Furthermore, even if local pressure is generated on the element 6 by the base plate bottom surface due to a decrease in the distance A due to a local thermal expansion difference on the spiral center side during pressure welding, the element 6 is locally moved into the groove 5. It can be absorbed, and accidents such as seizure caused by this can be prevented.

As described above, it has been found that if the element 6 is properly supported by the groove 5, it has the above advantages.
There have been cases where the parts have been locally abnormally worn or fallen into the grooves 5.

Therefore, the air 501 and the compression chamber P shown in FIG.
When the pressure was measured during each operation, the results shown in FIG. 14 were obtained. Here is a certain point B
Pressure fluctuation P ₁ in the sky = 501 from to point A
and the corresponding pressure fluctuation _P2 in the compression chamber P, and ΔP represents the differential pressure. Although it varies depending on the operating conditions and measurement points, the pressure P ₁ in the air 501 may be larger than the pressure P ₂ in the compression chamber P by ΔP as shown in a in the figure. At this time, the element 6 protrudes from the groove 5 and the base plates 102, 20
2 and will slide and wear out. Also, when P ₁ is smaller than P ₂ by △P as in b,
The element 6 will fall into the groove 5. Therefore, we came up with the idea of providing a conductive section between the compression chamber P and the air 501 to equalize the pressure. FIG. 15 shows a simple example of the starting end A and the ending end B of the element 6.
When a relatively large gap was provided between the corresponding ends of the grooves 5 as shown in the figure, the differential pressure ΔP between P ₁ and P ₂ became small as shown in FIG. 16.

As a further development, as shown in FIGS. 17 and 18, grooves 610 are appropriately provided in the axial direction on the side surface of the element 6 to appropriately conduct the air 501 and the chamber P along the longitudinal direction of the spiral. △P shown in Figure 16
The value of was further reduced and the pressure was almost equalized. Further, after long-term operation under these specifications, no wear or depression of the element 6 was observed.
It goes without saying that such a pressure equalizing groove may be provided on the groove 5 side. In addition, as another example, the first
As shown in FIGS. 9 and 20, a notch 510 may be provided in the groove 5 along the longitudinal direction of the spiral.

21 to 23 show still another embodiment, in which the elements 6 are divided and press-fitted along the longitudinal direction of the spiral, and gaps 611 are provided between each element 6. In this way, the length of the 61 elements can be shortened, so that workability can be improved.

FIG. 24 is designed to further increase stability in addition to preventing movement of the element 6 due to the pressure equalization described above, and this is done by making the groove 5 a different shape.

In FIG. 24a, the groove 5 is tapered as shown to prevent the element 6 from collapsing more than necessary. Further, b is designed to have a taper opposite to a to prevent sliding wear on the base plate 102 due to lifting of the element 6.

c is intended to provide a protrusion 512 on the cross section of the groove 5 to physically fix the element 6.

〔Effect of the invention〕

As explained above, according to the present invention, a plurality of fixed scrolls and oscillating scrolls, each formed by protruding a spiral side plate such as an involute on the base plate surface, are combined with each other, and a plurality of In a scroll fluid machine configured to compress or expand the fluid taken into the chamber by forming a chamber and rotating an oscillating scroll, the scroll has a spiral shape that is the same as each spiral side plate of both scrolls. and a guide groove formed along the end surface of the spiral side plates of both scrolls and into which the fine adjustment element is press-fitted, and a pair of fine adjustment elements having By adjusting the press-fitting depth, it is possible to finely adjust the distance between the end face of each of the fine adjustment elements and the corresponding bottom of the base plate, and also to adjust the distance between the fine adjustment element and the bottom of the guide groove. The present invention is characterized by having a distance fine adjustment mechanism configured to communicate the formed hollow portion with the spiral side plate or the end face side of the fine adjustment element at a plurality of locations.

Therefore, by press-fitting the fine adjustment elements evenly into the guide grooves provided on the end faces of the spiral side plates of the scroll, the fine adjustment elements can be used to adjust the end faces of each spiral side plate of the fixed scroll and the oscillating scroll through the fine adjustment elements. It is possible to make fine adjustments in the axial direction between the bottom surfaces of the base plate, eliminating variations in the machining accuracy of fixed scrolls, oscillating scrolls, etc., and with virtually no gaps or the minimum necessary minute adjustments. Adjustment is possible, and there is a hollow section in the axial direction between the fine adjustment element and the guide groove, and this hollow section is communicated with the spiral side plate or the end surface side of the element. Since the pressure between the chamber and the above-mentioned chamber, particularly its axially opposite end sides, is almost equalized, it is possible to prevent the fine adjustment element from moving in the axial direction due to pressure fluctuations in the chamber during operation. No force is generated in the axial direction, there is no frictional resistance or wear between the element and the base plate, and the element is fixed in a stable state without sinking into the guide part, resulting in a highly reliable spacer with little leakage. A fine adjustment mechanism is provided.

[Brief explanation of the drawing]

Fig. 1 is a sectional view of a scroll compressor equipped with a seal/fine adjustment assembly mechanism according to an embodiment of the present invention, Fig. 2 is an assembly view of the same, and Figs. 3 to 6 show the structure and operation of an eccentric bushing. FIG. 7 is an assembly perspective view when this embodiment is applied to an oscillating scroll, FIGS. 8 to 13 are partial schematic views explaining other assembly methods, and FIG. The pressure diagram before the improvement of this embodiment, FIG. 15 is a perspective view of the oscillating scroll after the improvement of this embodiment, FIG. 16 is the pressure diagram after the improvement of this embodiment, and FIGS. 17 to 24 are the invention of the present invention. FIG. 25 is a diagram of the operating principle of the scroll fluid machine, FIG. 26 is a sectional view of a conventional example, and FIGS. 27 to 30 are partial sectional views of other conventional examples. It is. In the figure, 1 is a fixed scroll, 2 is an oscillating scroll, 5 is a groove, 6 is a fine adjustment element, 101,
102 is a spiral side plate, 101a and 201a are end faces, 102 and 202 are base plates, 10 is a shim, and 51
0,610 is a pressure equalizing groove, and 611 is a gap.

Claims (1)

[Claims] 1 A fixed scroll and an oscillating scroll each formed by protruding a spiral side plate such as an involute from the base plate surface are combined with each other to form a plurality of chambers between each of the spiral side plates and the base plate surface, and the oscillating scroll is A scroll fluid machine configured to compress or expand fluid taken into the chamber by rotating a scroll, a pair of fine adjustment elements each having a spiral shape having the same shape as each spiral side plate of both scrolls; , a guide groove formed along the end surface of the spiral side plate of both scrolls, into which the fine adjustment element is press-fitted, and by adjusting the press-fit depth of each fine adjustment element into each of the guide grooves, The space between the end face of each of the fine adjustment elements and the corresponding bottom of the base plate can be finely adjusted, and the space formed between the fine adjustment element and the bottom of the guide groove.
A scroll fluid machine having a fine adjustment mechanism configured such that the part and the end face side of the spiral side plate or the fine adjustment element communicate with each other at a plurality of locations.