JPH08193581A - Scroll fluid machinery - Google Patents

Abstract

(57) [Summary] In a scroll fluid machine in which the non-orbiting scroll member 2 is axially movable, a non-orbiting reference surface 2u, which is a support surface of the non-orbiting scroll member 2 of the stopper member 7, is widened to the inner diameter side. . Further, in the scroll fluid machine in which the thrust member 9 is movable in the axial direction, the shape of the stopper member is simplified. Further, by introducing oil into the back space of the thrust member 9, the axial movement distance of the thrust member 9 is suppressed. [Effect] It is possible to provide a scroll fluid machine having high reliability, high efficiency, and excellent mass productivity.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a scroll fluid machine in which one scroll member is non-orbiting and the other scroll member is orbiting without rotating, and receives a thrust load on its back surface.

[0002]

2. Description of the Related Art Conventionally, a scroll fluid machine in which a non-orbiting scroll member movable in the axial direction and an orbiting scroll member are engaged with each other to receive a thrust load of compressed gas on the back surface of the orbiting scroll member is disclosed in Japanese Patent Application Laid-Open No. 5-263776. When the orbiting scroll member is incorporated into the compressor body as in the first prior art, an opening having a size that allows the orbiting scroll member to pass through the non-orbiting facing surface that supports the non-orbiting scroll in order to incorporate it from above. Was provided. Also,
In the second conventional technique shown in FIGS. 15 and 16, the non-swirl reference surface and the thrust reference surface are the same surface, so that the stopper member needs to have a portion connecting the non-swirl reference surface facing surface and the thrust reference surface facing surface. It was

[0003]

SUMMARY OF THE INVENTION In the first prior art,
No consideration has been given to the fact that the inner diameter of the annular non-orbiting facing surface is enlarged and the support point of the non-orbiting scroll member is far from the center of the non-orbiting scroll. The end plate of both scroll wraps comes into contact with each other due to the large bending of the end plate of the above, causing a problem that compression efficiency and reliability are deteriorated. Further, in the second conventional technique, the problem that the stopper member becomes large in the radial direction is not taken into consideration, and there is a problem that the miniaturization of the fluid machine is prevented.

The first object of the present invention is to solve the problems of the prior art.

A second object of the present invention is to provide a scroll fluid machine having improved workability in addition to the first object.

A third object of the present invention is, in addition to the second object, to provide a scroll fluid machine having small variations in performance and reliability during mass production.

A fourth object of the present invention is to provide, in addition to the second or third object, a scroll fluid machine having small variations in performance and reliability during mass production.

A fifth object of the present invention is to provide a scroll fluid machine having a simple structure and improved workability.

A sixth object of the present invention is, in addition to the fifth object, to provide a scroll fluid machine having a further improved workability and a reduced number of parts.

A seventh object of the present invention is, in addition to the fifth or sixth object, to provide a scroll fluid machine in which variations in performance and reliability during mass production are small.

An eighth object of the present invention is to provide a scroll fluid machine which exhibits stable compressor performance and has a wide range of operating conditions.

A ninth object of the present invention is to provide a scroll fluid machine having improved workability in addition to the eighth object.

[0013]

To achieve the first object, in order to achieve the first object, there is provided an orbiting scroll member which makes an orbiting movement with respect to the casing without rotation, an end plate and a scroll wrap standing upright on the orbiting scroll surface. A pump unit that forms a compression chamber by engaging a non-orbiting scroll member that is capable of parallel translation in an axial direction that is a direction perpendicular to A drive unit that realizes the orbiting movement of the orbiting scroll member, and a thrust member that forms a thrust bearing facing the orbiting rear surface of the orbiting scroll member that does not stand a scroll wrap and that is fixedly arranged with respect to the casing; And an approaching force in a direction that causes the non-orbiting scroll member to approach the thrust member, and the non-orbiting scroll portion in the axial direction. And a scroll fluid machine having a distance defining mechanism that defines a minimum distance between the thrust member and the non-orbiting reference surface of the non-orbiting scroll member in the same direction as the scroll wrap bottom of the non-orbiting scroll member. A thrust reference surface on the thrust bearing side is provided at a position apart from the non-orbiting reference surface in the thrust member in a direction from the tooth bottom of the non-orbiting scroll toward the tooth tip by a distance greater than 0.
A scroll lap insertion hole in a non-orbiting facing surface of the stopper member that is fixedly arranged with respect to the casing and is sandwiched between the thrust reference surface and the non-orbiting reference surface, and that faces the non-orbiting reference surface. Was set to a size such that the orbiting scroll member cannot pass through.

In order to achieve the second object, together with the means for achieving the first object, the non-orbiting reference surface of the non-orbiting scroll member is perpendicular to the axial direction, and the thrust member is provided. The thrust reference plane in was set perpendicular to the axial direction.

Further, in order to achieve the third object,
Along with the means for achieving the second object, the non-orbiting reference surface and the scroll wrap tooth bottom surface of the non-orbiting scroll member are flush with each other.

Further, in order to achieve the fourth object,
Together with the means to achieve the second or third purpose,
The thrust bearing of the thrust member is a slide bearing, and the slide bearing surface and the thrust reference surface are the same surface.

Further, in order to achieve the fifth object,
It has a revolving scroll member that makes a revolving motion without rotation with respect to the casing, an end plate, and a scroll wrap standing upright on the revolving scroll member. It is possible to move in the axial direction, which is the direction perpendicular to the revolving surface, but parallel to other directions. It comprises a pump section that forms a compression chamber by engaging a non-orbiting scroll member that is almost incapable of movement and all rotational movements, and a drive section that realizes the orbiting movement of the orbiting scroll member, and the scroll is the end plate of the orbiting scroll member. A thrust member that is opposed to a revolving rear surface without a wrap and is movable in an axial direction that is a direction perpendicular to the revolving movement surface with respect to the casing; and the thrust member in the axial direction. An approaching force for approaching the non-orbiting scroll member, and the non-orbiting scroll member and the thrust portion in the axial direction. In the scroll fluid machine having a distance defining mechanism that defines a minimum distance of the non-orbiting reference surface in the same direction as the scroll wrap tooth bottom of the non-orbiting scroll member in the non-orbiting scroll member, The thrust member has a thrust reference surface on the side of the thrust bearing, and a stopper member fixedly arranged with respect to the thrust member is provided between the thrust reference surface and the non-orbiting reference surface.

Further, in order to achieve the sixth object,
The thrust member is integrated with the stopper member together with the means for achieving the fifth object.

In order to achieve the seventh object,
Along with the means for achieving the fifth or sixth object, the non-orbiting reference surface and the scroll wrap tooth bottom surface or tooth tip surface of the non-orbiting scroll member are made the same surface.

Further, in order to achieve the eighth object,
It has a revolving scroll member that makes a revolving motion without rotation with respect to the casing, an end plate, and a scroll wrap standing upright on the revolving scroll member. It is possible to move in the axial direction, which is the direction perpendicular to the revolving surface, but parallel to other directions. It comprises a pump section that forms a compression chamber by engaging a non-orbiting scroll member that is almost incapable of movement and all rotational movements, and a drive section that realizes the orbiting movement of the orbiting scroll member, and the scroll is the end plate of the orbiting scroll member. A thrust member that is opposed to a revolving rear surface without a wrap and is movable in an axial direction that is a direction perpendicular to the revolving movement surface with respect to the casing; and the thrust member in the axial direction. An approaching force for approaching the non-orbiting scroll member, and the non-orbiting scroll member and the thrust portion in the axial direction. In the scroll fluid machine having a distance defined mechanism for defining the minimum distance slightly but in communication with the outside world is provided a thrust back space which is a space closed outline on the opposite side of the thrust bearing of the thrust member,
The approaching force was given by introducing oil having a pressure higher than the suction pressure therein.

Further, in order to achieve the ninth object, the scroll compressor is of a horizontal type together with the means for achieving the eighth object.

[0022]

In the scroll fluid machine having the stopper member and the non-orbiting scroll member movable in the axial direction, the end plate of the non-orbiting scroll is bent due to the approaching force applied to the back surface of the non-orbiting scroll, and the tooth tip roots of both scroll wraps. If the initial clearance between them is small, there is a risk of pressure contact between the tooth tips and the roots. This amount of deflection increases rapidly as the span of the support points of the non-orbiting scroll increases. Among the means for achieving the first object, by providing a scroll wrap insertion hole having a size in which the orbiting scroll member cannot pass through on the non-orbiting facing surface, the scroll wrap insertion enlarged until the orbiting scroll member can pass through. Since the span of the supporting points of the non-orbiting scroll member with respect to the approaching force is smaller than that in the case where the holes are provided, the bending of the end plate of the non-orbiting scroll member can be suppressed. Therefore, it is possible to reduce the initial gap between the tip and the bottom of the scroll wrap,
It is possible to reduce the gap while avoiding contact between the tooth tops at the time of actual operation, improving reliability, suppressing internal leakage between the tooth tops, and improving compression efficiency. Further, since the stopper member has a shape in which the thrust reference surface facing surface is provided near one end in the axial direction and the non-turning reference surface facing surface is provided near the other end, the stopper reference surface and the non-turning reference surface like the second type are provided. The part that connects the facing surfaces is unnecessary,
The fluid machine can be miniaturized.

By the means for achieving the second object, in addition to the effect of the means for achieving the first object, the surface of the stopper member facing the thrust reference surface and the surface of the stopper member facing the non-turning reference surface are parallel to each other. It is possible to improve the sex.

Further, by means of achieving the third object,
In addition to the effect of the means for achieving the second object, the number of dimensions for determining the initial setting clearance between the scroll wrap addendums and the roots is reduced, and the variation of the initial setting clearance at the time of mass production can be reduced. Variation can be reduced.

Further, by means of achieving the fourth object,
In addition to the effect of the means for achieving the second or third purpose, the number of dimensions that determine the initial setting clearance between the scroll wrap addendums and the roots is reduced in places other than the means for achieving the third purpose. Since variations in the initial setting gap can be reduced, variations in performance and reliability during mass production can be reduced.

The fluid machine in which the non-orbiting scroll member is fixed and the thrust member is axially movable has an extremely simple structure as compared with the fluid machine having the axially movable non-orbiting scroll member. This is because in the latter case, movement of the non-orbiting scroll member, which is an axially movable member, in a direction other than the axial direction cannot be permitted, so a parallel movement prevention mechanism in the orbiting motion plane and a rotation stopping mechanism around the movable axial direction are required. , In the former, since the parallel movement in all directions and the rotational movement around the axial direction of the thrust member, which is the axially movable member, are allowed,
This is because the parallel movement prevention mechanism in the plane of the turning motion and the rotation stopping mechanism around the movable axis are unnecessary. Therefore, by the means for achieving the fifth object, the structure is extremely simple and the workability is high as compared with the fluid machine having the non-orbiting scroll member which is movable in the axial direction, and the thrust reference surface facing surface of the stopper member is provided. Since the surfaces opposite to the non-turning reference surface are parallel to each other, the workability of the stopper member can be improved.

Further, by means of achieving the sixth object,
In addition to the effect of the means for achieving the fifth object, the number of parts can be reduced, and the surface facing the thrust reference surface of the stopper member and the thrust bearing are provided in parallel with each other in the same direction of the thrust member, which improves workability. Can be achieved.

Further, by means of achieving the seventh object,
In addition to the effect of the means for achieving the fifth or sixth object, the number of dimensions that determine the initial setting gap between the scroll wrap addendums and the roots is reduced, and the variation in the initial setting gap during mass production can be reduced. It is possible to reduce variations in the performance and reliability of.

The axial load received by the thrust member from the orbiting scroll member varies with the rotational phase of the shaft. In particular, the fluctuation range becomes large during over-compression or under-compression operation. Therefore, in principle, it is necessary to set the approaching force larger than the maximum axial load. However, if this is done faithfully, the setting level of the approach force will be extremely high, and the load between the tooth tops of the scroll wraps will be very large when pressure contact between the tooth tops of the scroll wrap is avoided, The reliability decreases. Therefore, usually, a design is made so that the approach force is slightly insufficient at the peak of the load fluctuation due to the rotation of the shaft during the over-compression or the under-compression operation in which the fluctuation range becomes large. This is because if the time when the approaching force is insufficient is short, the moving distance of the thrust member is small and the compression performance is slightly deteriorated. According to the means for achieving the eighth object, the back space of the thrust member and the oil in the thrust member play a role of a damper in the axial movement of the thrust member, so that the moving distance of the thrust member becomes small when the approaching force is insufficient. The reduction range of compression performance is also small. From a different point of view, this means expanding a highly reliable and highly efficient operating range.

By means of achieving the ninth object,
In addition to the effect of the means for achieving the eighth object, since the fluid machine is placed horizontally, the oil in the casing accumulates over the entire axial direction, which shortens the distance between the thrust back space and the oil in the casing. In addition, since the oil guide passage to the thrust back space can be easily installed, the workability is improved.

[0031]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS A first embodiment in which the present invention is applied to a non-orbiting float type scroll compressor in which a non-orbiting scroll member is axially movable will be described with reference to FIGS. 1 and 3 to 14. 1 is a longitudinal sectional view of the compressor, FIG. 3 is a perspective view of the orbiting scroll member from above, FIG. 4 is a perspective view of the orbiting scroll member from below, and FIG. 5 is a perspective view of the non-orbiting scroll member from above. 6 is a perspective view of the non-orbiting scroll member from below, FIG. 7 is a plan view of the bottom surface of the non-orbiting scroll member, FIG. 8 is a top view of the orbiting scroll member, and FIG. 9 is FIG.
FIG. 10 is a perspective view of the Oldham ring from above, FIG. 11 is a perspective view of the stopper member from above, FIG. 12 is a top view of the stopper member, and FIG. 13 is an explanation of the oil groove position. FIG. 14 shows a top view of the non-orbiting scroll member.

In the orbiting scroll member 3, a scroll wrap 3b is erected on the upper surface of an end plate 3a, a boss 3c is arranged at the center of the lower surface, and a thrust surface 3d is arranged on the outer peripheral portion of the lower surface. The Oldham projections 3e and 3f are provided on the outer periphery of the end plate 3a.
Is projected, and turning Oldham grooves 3g and 3h are provided therein. Further, Oldham support protrusions 3i and 3j are provided on the outer peripheral portion of the end plate 3a. The scroll wrap 3b has a thickness that decreases from the center toward the outer periphery, except for the center side end portion 3l and the outer peripheral side end portion 3m. Here, the thickness of the scroll wrap 3b is the length of line segments A1 and B1 at which the angles α and β formed by the wrap outer line and the wrap inner line are equal, as shown in FIG. Further, in order to balance the scroll wrap 3b, a balance cutout portion 3k is formed by linearly cutting the top surface of the end plate 3a. End plate 3
Since the outer periphery of the lower surface of a has a cylindrical shape, it can be used as a chucking surface during scroll wrap processing or during transportation. Therefore, handling during processing becomes easy, and the workability of the compressor can be improved.

The stopper member 7 is provided with two planes which are parallel to each other and serve as a non-turning reference surface facing surface 7f on the upper surface and a thrust reference surface facing surface 7g on the lower surface. As a result, the workability of this stopper member is improved. In addition, a scroll lap insertion hole 7i having a size such that the orbiting scroll member 3 cannot pass through is formed in the center of the non-orbiting reference surface facing surface 7f. A large opening is provided in the lower part of the stopper member 7 because a space for the orbiting scroll member 3 to orbit is required. As a result, an overhang portion 7h is formed above the stopper member 7. Rotation stop grooves 7a and 7b are provided on the upper portion of the overhang portion 7h, and fixed Oldham grooves 7c and 7d are provided on the lower portion. This rotation stop groove 7
The a and 7b and the fixed Oldham grooves 7c and 7d have a common side surface. In addition, the scroll wrap 3b accompanying the turning motion
Overhang part 7h to avoid interference with the outer periphery of
An inner peripheral cutout portion 7e is provided at. Further, inner peripheral grooves 7x and 7y are provided on the inner peripheral surface of the lower portion of the overhang portion 7h as a relief of the Oldham protrusions 3e and 3f of the orbiting scroll 3. Further, the outer peripheral surface is provided with a flow groove 7z which serves as a flow path for gas and oil. A suction hole 7s is provided on the side surface.

In the non-orbiting scroll member 2, a scroll wrap 2b is erected on the lower surface of an end plate 2a, and a seal protrusion 2c is erected on the center of the upper surface. A non-turning reference surface 2u, which is the same surface as the bottom surface of the scroll wrap tooth, is provided on the outer peripheral portion of the lower surface of the end plate 2a. In addition, a discharge hole 2d and two release holes 2e for preventing overcompression are opened near the center inside the seal projection 2c. The release valve 23 (two-dot chain line in FIG. 14) integrated so as to cover the release hole 2e is fixed by the release screw 50. Here, the method of fixing the release valve 23 and the float scroll 2 may be caulking pins, bonding, welding or silver brazing instead of screwing. The release hole 2e opens on the same surface as the screw hole 2i of the release screw 50 (hatched portion in FIG. 14). Further, a pressure equalizing hole 2f is opened outside the seal protrusion 2c.
Rotation stoppers 2g and 2h project from the lower surface of the end plate 2a. The scroll wrap 2b has a thickness that decreases from the center toward the outer periphery, except for the center-side end portion 2l and the outer-periphery-side end portion 2m. Here, under the condition of frequent operation, it is not necessary for the non-orbiting scroll member 2 to move upward, and the non-orbiting reference surface 2u is pressed against the non-orbiting reference surface facing surface 7f. Set the height.

The thrust member is integrated with the frame 4. The upper portion of the frame 4 is provided with the slide thrust bearing 9a of the thrust portion and the thrust reference surface 9b on the same surface. An oil groove 4b is provided on the slide thrust bearing 9a, and an oil supply hole 4c communicating with the rear chamber 11 is opened therein. In the present embodiment, there are four, but the back chamber 11
When it is desired to increase the pressure of, the number of the oil supply holes 4c is reduced or narrowed. Further, the outer peripheral surface is provided with a flow groove 4h serving as a flow path for gas and oil. Further, a main bearing 4a is provided in the central portion.

The Oldham ring 5 has a fixed protrusion 5 on the upper surface.
a and 5b are provided, and turning projections 5c and 5d are provided on the lower surface.

The float rail member 25 has a rail surface 2 on the lower inner periphery which serves as a track for vertical movement of the non-orbiting scroll member 2.
5c, a cover retainer 25a is provided on the upper portion, and a ring groove 25b is provided on the inner peripheral portion. A seal ring 51 made of a heat resistant and flexible material is inserted into the ring groove 25.

The shaft 12 is internally provided with a shaft oil supply hole 1
2a and a lateral oil supply hole 12b are provided. Further, a bearing holding portion 12f having an enlarged diameter is provided on the upper portion thereof, a slewing bearing 12c is press-fitted into the bearing holding portion 12f at an eccentric position, and an oil supply pipe 12d is fixed to the lower end portion.

The rotor 15 has a non-magnetized permanent magnet 15b built in a laminated steel plate 15a, and an upper balance weight 1 on the upper surface.
Fix 5c. Here, in order to make the balance weight 15c into a cylindrical shape, the upper correction balance weight 15e made of a material having a smaller specific gravity than the balance weight 15c is fixed to the upper balance weight 15c. Further, the lower balance weight 15d is fixed to the lower surface. Here, in order to make the lower balance weight 15d into a cylindrical shape, the lower correction balance weight 15f made of a material having a smaller specific gravity than the lower balance weight 15d is used as the lower balance weight 1
Fix at 5d. Balance weight 15c as a material,
15d is zinc or brass, compensating balance weight 15
Aluminum alloys may be used for e and 15f. Further, the correction balance weights 15e and 15f may be directly fixed to the laminated steel plate 15a. Further, the plate may be used as the correction balance weights 15e and 15f having a hollow inside. In this case, the total weight of the balance weight and the correction balance weight is reduced, and the compressor can be made smaller and lighter.

The stator 16 is provided with an oil groove 16c on the outer peripheral portion of a laminated steel plate 16b. By the way, this oil groove 16
Instead of c, a vertical hole serving as an oil passage may be formed inside the laminated steel plate 16b.

A compressor is constructed by assembling the above elements as follows.

First, the shaft 12 is inserted into the main bearing 4a of the frame 4 and the rotor 15 is fixed. Next, the orbiting scroll member 3 is assembled by inserting the boss 3c into the orbiting bearing 12c and mounting the thrust surface 3d on the sliding thrust bearing 9a of the frame 4. At this time, a rear chamber 11 is formed on the rear surface of the orbiting scroll member 3. Next, Oldham Ring 5
To the swiveling Oldham grooves 3g and 3h.
Is placed on the upper surface of the end plate 3a. Next, the fixed protrusions 5a and 5b are fixed to the fixed Oldham grooves 7c and 7d.
Then, the surface 7g facing the thrust reference surface is placed on the thrust reference surface 9b which is the same surface as the sliding thrust bearing 9a, and the stopper member 7 is incorporated. At this time, a suction chamber 60 is formed around the orbiting scroll member 3. Further, the rotation stoppers 2g and 2h are inserted into the rotation stopper grooves 7a and 7b, and the scroll wrap 2b is inserted into the scroll lap insertion hole 7i, and the non-orbiting reference surface 2u, which is the same surface as the tooth bottom of the scroll wrap 2b, is the non-orbiting reference. The non-orbiting scroll member 8 is mounted on the surface facing surface 7f. As a result, the dimensions that determine the gap between the scroll wrap addendums and bottoms that greatly affect the performance of the compressor are 4 scroll wrap heights, the thickness of the end plate 3a of the orbiting scroll member, and the height of the stopper member.
Since it is narrowed down to individual pieces, it is possible to suppress variations in the setting gap between the scroll wrap addendums and bottoms during mass production, and to reduce variations in performance and reliability. Next, the rail surface 25
c is along the outer peripheral surface of the non-orbiting scroll member 2, and the seal ring 51 arranged in the ring groove 25b is slid on the outer peripheral surface of the seal projection 2c, and the float rail member 25 is placed on the stopper member 7. . At this time, the outer circumference of the non-orbiting scroll member 2 and the rail surface 25c have a clearance fit of about 5 μm in diameter difference. Further, the cover retainer 25a prevents the center cover 24 from coming off the inner circumference of the seal protrusion 2c. After incorporating each element as described above, the stopper member 7 and the float rail member 25 are fixed to the frame 4 by the cover screw 53 while rotating the shaft 12 or the rotor 15. At this time, the upper chamber 10 is formed between the upper surface of the non-orbiting scroll member 2 and the float rail member 25.

The frame 4 is inserted and fixed in the cylindrical casing 1 in which the stator 16 is shrink-fitted or press-fitted in advance. At this time, the wiring 16a extending from the stator 16 is passed through one of the flow grooves 4h and 7z to bring the wiring terminal to the upper portion of the frame 4. And the suction pipe 54
Is inserted into the suction hole 7s and fixed. Next, the upper casing 20 to which the hermetic terminal 22 is previously welded is inserted into the internal terminal of the hermetic terminal 22, and then the wiring terminal of the wiring 16 a is inserted, and then fixed to the cylindrical casing 1. At this time, an upper chamber 61 is formed on the outer peripheral cover 25. Next, the bearing support 18 to which the sub bearing 17 is fixed in advance is fixed to the cylindrical casing 1 by inserting the lower portion of the shaft 12 into the inner ring of the sub bearing 17. In this state, an electric current is passed through the stator 16 and the permanent magnet 1 inside the rotor 15
5b is magnetized to form the motor 19. Furthermore, the lower casing 21 is fixed to the cylindrical casing 1, and the discharge pipe 5
5 is fixed to the cylindrical casing 1. At this time, frame 4
A motor chamber 62 is formed between the lower cover 21 and the lower cover 21.
Finally, the lubricating oil 56 is added.

The gas sucked from the suction pipe 54 into the suction chamber 60 is compressed in the compression chamber 6 by the orbiting motion of the orbiting scroll member 3 and discharged from the discharge hole 2d to the upper chamber 61 above the non-orbiting scroll member 2. To be done. The gas once enters the motor chamber 62, separates the motor cooling and the lubricating oil contained in the gas, and then flows out of the compressor through the discharge pipe 55. Under an operating condition where the pressure ratio is low, the release valve 23 works to avoid overcompression. At this time, the central cover 24 defines the maximum opening degree of the release valve 23.
The orbiting scroll member 3 receives a force in a direction in which it separates from the non-orbiting scroll member 2 due to the gas inside the compression chamber 6, but the thrust surface 3d is supported by the sliding thrust bearing 9a. Are separated. Similarly, the non-orbiting scroll member 2 receives a force in a direction in which it is separated from the orbiting scroll member 3 by the gas inside the compression chamber 6, but due to the approaching force due to the discharge pressure applied to the inside of the outer peripheral portion of the seal protrusion 2c, the scroll Axial separation of the members 2, 3 is avoided. Since the thrust surface 3d is supported by the sliding thrust bearing 9a, the axial separation of the scroll members 2 and 3 is avoided. As a result, the compression operation can be continued without expanding the gap between the tooth top and the tooth bottom of the scroll member. Here, the non-turning reference surface facing surface 7f
Since it is the upper surface of the overhang portion 7h, the span of the supporting point of the non-orbiting scroll member 2 with respect to the approaching force becomes small, and the deflection of the end plate 2a can be suppressed. As a result, the compression performance can be improved. The inner line and the outer line of the scroll wraps 2b and 3b of the non-orbiting scroll member 2 connect the points separated by the same distance from an arbitrary point on the spiral whose distance from the origin increases in a convex state with an increase in declination. Is used. Here, a point separated from the arbitrary point A on the spiral line S by the same distance b is a point separated from the spiral line S by b on the normal line of the point A. As described above, a spiral whose distance from the origin increases in an upwardly convex state with an increase in declination is, for example, an algebraic spiral or a logarithmic spiral, or a distance from the origin follows a hyperbola with an increase in declination. A spiral that increases with changes is conceivable. Also, a curve formed by continuously connecting a plurality of curves in a piecewise fashion such as a spline interpolation curve may be used. As a result, the thickness decreases from the central portion toward the outer peripheral portion. Therefore, as compared with the conventional scroll wrap having a uniform wrap thickness, the outermost peripheral position where the scroll wrap is erected can be set closer to the center by the amount by which the wrap thickness of the outer peripheral portion of the wrap is reduced. Therefore, the scroll wrap diameter can be reduced, and the compressor can be reduced in size and weight. Furthermore, this also makes it possible to greatly reduce the axial load on the thrust surface 3d. Therefore, the friction loss at that portion can be reduced, and the compressor can be highly efficient. Further, since the non-orbiting scroll member 2 movable in the vertical direction is used, even if the tip and bottom of the wrap are pressed against each other due to the deformation of the scroll wrap during actual operation, the non-orbiting scroll member 2 moves upward, No pressure contact between tip and root. Further, due to the thermal expansion of the central portion of the wrap due to the high temperature, the position where the tooth tips and bottoms come into contact is the central portion of the lap, but since the central lap is thick, the reliability of the compressor can be secured. Further, since the stopper member 7 is used, it is possible to operate without frequent contact between the tooth tops of the laps under the condition of frequent operation. Therefore, since the friction loss at that portion can be reduced, the efficiency of the compressor can be improved. Further, since the familiar surface film is provided on the orbiting scroll member 3 without covering the thrust surface 3d, a high-performance compressor can be easily machined. Further, since the downward force applied to the non-orbiting scroll member 2 is applied by the discharge pressure applied to the inner peripheral portion of the seal protrusion 2c, no dedicated component is required and the number of compressor components can be reduced. Further, since the outer peripheral portion of the seal projection 2c has the suction pressure, the central portion of the upper surface of the end plate 2a has the discharge pressure and the outer peripheral portion has the suction pressure. Therefore, the end plate 2
Since the lower surface and the upper surface of a have the same pressure distribution, pressure deformation of the end plate 2a is suppressed. As a result, the compressor can be highly efficient over a wide operating range. Further, since the release valve is provided, the efficiency can be improved even under the operating condition where the pressure ratio is low. Also, since the Oldham ring 5 is placed on the upper surface of the end plate 3a,
The diameter of the compressor can be reduced.

The lubricating oil 56 accumulated at the bottom of the compressor is discharged by the motor chamber 62 and the suction chamber 6 by the oil supply hole 4c.
Owing to the pressure difference of the suction pressure of the back chamber 11 which is continuous with 0, oil is supplied to the orbiting bearing 12c through the shaft oil supply hole 12a. In addition, the main bearing 4a passes through the lateral oil supply hole 12b.
Is refueled. The lubricating oil 56 enters the oil groove 4b through the back pressure chamber 11 and the oil supply hole 4c, and a part thereof lubricates the sliding thrust bearing 9a. As shown in FIG. 13, the oil groove 4b is always connected to the suction chamber 60 at one location, so that the lubricating oil 56 always enters the suction chamber 60. Then, the gas enters the compression chamber 6 together with the gas, and the discharge hole 2 together with the compressed gas.
It is discharged from d to the upper chamber 61. Then, the motor room 62
It is separated from the gas at and finally returns to the bottom of the compressor. By the way, the oil groove 4b may be a circle eccentric from the center of the main bearing. In this case, the oil groove 4b is blocked from the suction chamber 60 at the eccentric angle, and the pressure in the back chamber 11 increases.
Therefore, by eccentricizing the center of the oil groove 4b to the center position of the slewing bearing when the load applied to the thrust surface 3d becomes large, the load applied to the thrust surface 3d can be made uniform.
As a result, the reliability of the compressor can be improved. In addition, as a result of refueling the orbiting bearing 12c and the sliding thrust bearing 9a,
Since the back surface of the boss 3c has the discharge pressure, the discharge pressure is applied to the central portion of the rear surface of the orbiting scroll member 3, and the load on the sliding thrust bearing 9a can be reduced. Therefore, since the friction loss there can be reduced, the compressor becomes highly efficient. Further, since the back chamber 11 has a suction pressure, the central portion of the lower surface of the end plate 3a has a discharge pressure and the outer peripheral portion has a suction pressure. Therefore, since the lower surface and the upper surface of the end plate 3a have similar pressure distributions, the pressure deformation of the end plate 3a is suppressed. As a result,
The compressor can be highly efficient over a wide operating range.

The lubricating oil 56 in the rear chamber 11 is constantly discharged, and the viscous loss due to the rotation of the swivel holder 12f can be reduced. Further, since the swivel holding portion 12f has a cylindrical shape, the viscosity loss due to the rotation of the swivel holding portion 12f can be further reduced. Further, since the central cover 24 and the float rail member 25 form a gas layer in the lower portion thereof, heat from the hot discharge gas in the upper chamber 61 is prevented from being transferred to the compression chamber 6. Further, the center cover 24 and the float rail member 25 block the impact sound that accompanies the opening and closing of the release valve 23. Furthermore, since the side surfaces of the rotation stopping grooves 7a and 7b and the Oldham grooves 7c and 7d are the same, simultaneous processing is possible, and the accuracy of the angular relationship between them is improved. Further, since the rotation stoppers 2g and 2h are integrally formed on the end plate, the accuracy of the positional relationship with the scroll wrap 2b is improved. By the way, as a result of the scroll wraps 2b, 3b attempting to fall toward the outer circumference due to the gas pressure received on the side surfaces of the scroll wraps 2b, 3b, the end plates 2a, 3a are bent,
The gap between laps expands. On average, the curve of the end plate has a mode in which the line passing through the center of the end plate and the end of the scroll wrap is the peak. In the present embodiment, since the Oldham support protrusions 3i and 3j are provided at this position,
The deformation of the end plate 3a is suppressed. Further, since the outer circumference of the release valve 23 has substantially the same size as the inner circumference of the seal projection 2c, the positioning of the release valve 23 is easy.

Further, the upper surface of the end plate 3a of the orbiting scroll member 3 and the entire surface of the scroll wrap 3b may be provided with a surface coating having conformability and lubricity. For example, a surface coating formed by nitrosulphurizing treatment or manganese phosphate coating treatment is conceivable. As a result, the gaps between the side surfaces of the scroll wraps 3b and 2b and between the tooth tops can be reduced, and the slidability at the contact portions of the scroll wraps 3b and 2b can be improved, so internal leakage is reduced and friction loss can be reduced.
As a result, the performance of the compressor can be improved.

The end plate 2a of the non-orbiting scroll member 2
A surface coating having conformability and lubricity may be provided on the lower surface of and the entire surface of the scroll wrap 2b. For example,
Surface coating by nitrosulphurizing treatment or manganese phosphate coating treatment is considered. Thereby, the scroll wraps 3b, 2b
Since it is possible to reduce the gap between the side surfaces and between the tooth tops and the tooth bottoms and further improve the slidability at the contact portion of the scroll wraps 3b and 2b, internal leakage is reduced and friction loss is reduced. As a result, the performance of the compressor can be improved.

Further, the upper surface of the end plate 3a of the orbiting scroll member 3 and the entire surface of the scroll wrap 3b, and the lower surface of the end plate 2a of the non-orbiting scroll member 2 and the entire surface of the scroll wrap 2b have conformability and lubricity. A surface coating may be provided. For example, a surface coating formed by nitrosulphurizing treatment or manganese phosphate coating treatment is conceivable. As a result, the gap between the side surfaces of the scroll wraps 3b and 2b and between the tooth tops and the tooth tops can be easily reduced, and the scroll wrap 3
Since the slidability at the contact portions of b and 2b can be further improved, internal leakage can be reduced and friction loss can be reduced. As a result, the familiar operation period of the compressor can be shortened and the performance can be further improved.

It is also conceivable to provide a surface coating whose thickness decreases with time on the surface of the non-turning reference surface 2u which is in contact with the non-turning reference surface facing surface 7f. As a result, the tooth tops and the tooth bottoms of both scroll members 2 and 3 approach each other over time, so that the tooth tip roots caused by the accidental wear between the tooth tip roots of both scroll members 2 and 3 occur. The gap between them can be reduced, and high performance can be maintained over a long period of time. As such a coating, for example, a surface coating obtained by a nitrosulfurization treatment or a manganese phosphate coating treatment can be considered. Since these coatings have pores inside, if pressure is applied and held for a long time, the pores inside will gradually collapse, and the thickness will decrease with time.

Further, it is conceivable to provide a surface coating which easily wears on the surface of the non-turning reference surface 2u which is in contact with the non-turning reference surface facing surface 7f. The non-orbiting scroll member 2 can move relative to the teeth of the stopper member 7 along the rotation stop grooves 7a and 7b by a diameter gap between the outer periphery of the non-orbiting scroll member 2 and the rail surface 25c. In fact, the horizontal force of the compressed gas causes them to move relative to each other. This is because the non-turning reference surface facing surface 7f and the non-turning reference surface 2u rub against each other, and the surface coating of the non-turning reference surface 2u wears little by little. As a result, the tooth tops and the tooth bottoms of both scroll members 2 and 3 approach each other over time, and the tooth tip tooth roots caused by the accidental wear between the tooth tip roots of both scroll members 2 and 3 occur. The gap between them can be reduced, and high performance can be maintained over a long period of time. As such a coating, for example, a surface coating obtained by a nitrosulfurization treatment or a manganese phosphate coating treatment can be considered.

Further, the entire surface of the non-orbiting scroll member 2 may be provided with a surface coating by nitrosulfurizing treatment or manganese phosphate coating treatment. As a result, the coating process of the non-orbiting scroll member 2 can be performed without masking, and the gaps between the side surfaces of the scroll wraps 3b and 2b and between the tooth tips and bottoms of the scroll wraps 3b and 2b can be reduced to reduce the scroll wraps 3b and 2b.
Since the slidability at the contact portion of b can be improved and the tooth tops and bottoms of both scroll members 2 and 3 approach each other with time, accidental gaps between the tooth tops of both scroll members 2 and 3 will occur. It is possible to reduce the gap between the tooth tops and the tooth bottoms caused by the wear due to the approach. As a result, it is possible to easily create a compressor having high performance and capable of maintaining the high performance for a long period of time.

Further, after the surface coating of the non-orbiting scroll member 2 is formed by the nitrosulfurizing treatment or the manganese phosphate coating treatment, the same surface as the screw hole 2i (hatched portion in FIG. 14) is flattened. It may be ground into a shape. This allows
The release valve 23 reliably blocks the release hole 2f. As a result, the performance of the compressor under the overcompression condition can be improved.

The thrust surface 3d of the orbiting scroll member 3 may be provided with a wear-resistant surface coating, a wear-resistant structure by heat treatment, or a wear-resistant substance. As a result, the separation between the tooth tops of the scroll members 2 and 3 is suppressed, so that high performance can be maintained for a long period of time.

Further, the thrust surface 3d of the orbiting scroll member 3 may be provided with a surface film having good lubricity, a structure having good lubricity by heat treatment, or a substance having good lubricity.
As a result, the sliding loss of the thrust surface 3d is reduced, so that the performance of the compressor can be improved.

Further, the rotation stoppers 2g and 2h of the non-orbiting scroll member 2 are grooves, and the rotation stopper groove 7 of the stopper member 7 is used.
The protrusions may be a and 7b. In this case, since the strength of the stopper member 7 increases, the reliability of the compressor can be improved.

The central cover 24 may be made of a material having a coefficient of thermal expansion larger than that of the end plate 2a, and the outer circumference of the central cover 24 and the inner circumference of the seal projection 2c may be fitted with a clearance of about 10 μm at the maximum. In this case, the central cover 24 expands due to the temperature rise during operation, and deforms in the direction in which the seal projection 2c is expanded. As a result, the upper surface of the mirror plate 2a relatively extends as compared with the lower surface thereof, so that the mirror plate 2a is deformed to be convex upward. Therefore, it is possible to avoid contact between the wrap addendums and roots due to the high temperature of the central portion of the scroll wrap, and it is possible to realize high efficiency and high reliability of the compressor. For example, the non-orbiting scroll member 2 is made of cast iron, and the central cover 24 is made of brass, zinc, or aluminum alloy, and particularly 1 of silicon content.
It may be made of an aluminum alloy having a large Young's modulus of about 0 to 30%.

Further, the surface of the boss 3c of the orbiting scroll member 3 may be provided with a wear-resistant coating, a wear-resistant structure by heat treatment, or a wear-resistant substance. As a result, the durability of the boss 3c is improved, and the reliability of the compressor can be improved.

Further, the surface of the boss 3c of the orbiting scroll member 3 may be provided with a coating having good lubricity, a wear resistant structure by heat treatment or a wear resistant substance. As a result, sliding loss of the slewing bearing is reduced, so that the performance of the compressor can be improved.

Also, the boss 3c of the orbiting scroll member 3
Alternatively, another member made of a wear resistant material may be mechanically fixed or fixed by welding or adhesion. This facilitates the processing of the durable boss 3c, so that the workability of the compressor can be improved.

Further, the scroll wraps 2b and 3b may be formed by involute curves. As a result, the scroll wrap can be easily processed, and the workability of the compressor can be improved.

Next, a second embodiment of the present invention will be described. FIG. 17 is a longitudinal sectional view, FIG. 18 is a perspective view of the orbiting scroll member from above, FIG. 19 is a perspective view from below, and the Oldham ring. It will be described with reference to FIG. 20, which is a perspective view from above. Here, except that the Oldham ring 5 is arranged between the orbiting scroll member 3 and the frame 4, it is the same as the first embodiment, and therefore the description of the configuration and operation of the other parts will be omitted. Revolving Oldham grooves 3g and 3h are provided on the rear surface of the revolving scroll, and fixed Oldham grooves 4p and 4q (4q is not shown) are provided in the frame 4. As a result, it is not necessary to provide the orbiting Oldham groove on the outer peripheral portion of the orbiting scroll member, and the workability of the orbiting scroll member can be improved.
The outermost part of the fixed Oldham grooves 4p and 4q is the frame 4
Of the rear chamber 11 and the suction chamber 60 are constantly connected to guide the lubricating oil 56 flowing into the rear chamber 11 to the suction chamber 60 and to make the pressure of the rear chamber 11 almost the suction pressure.
As a result, a hole for connecting the back chamber 11 and the suction chamber 60 is not required, and the workability is improved. Furthermore, the end plate 3a
Since the chamfering of the outer peripheral corners of the upper surface can reduce the flow path resistance of the suction gas, the compression efficiency can be improved. Further, since the Oldham ring 5 is circular, the workability is improved.

Next, a third embodiment in which the present invention is applied to a thrust float type scroll compressor in which a non-orbiting scroll member is fixed to a casing and a thrust member is axially movable is shown in a longitudinal sectional view of FIG. It will be described based on.

The thrust member 9 is a sliding thrust bearing 9a.
A stopper portion 9f serving as a stopper member projects from the outer peripheral portion of the upper surface, and the upper surface serves as the non-turning reference surface facing surface 7f. As a result, since the thrust bearing 9a and the non-turning reference surface facing surface 7f are provided in parallel in the same direction, the lathe allows easy machining while accurately controlling the distance between these two surfaces. In addition, the distance between the thrust bearing 9a and the non-orbiting reference surface facing surface 7f is one of the dimensions that determines the clearance between the tooth top and the tooth bottom of the scroll wrap. It is possible to provide a scroll fluid machine with less variation in performance and reliability. An oil supply hole 9c is provided between the oil groove 9g provided in the sliding thrust bearing 9a and the rear chamber 11. A seal groove 9e is provided on the inner peripheral side and a seal groove 9d is provided on the outer peripheral side on the side surface, and seals 97 and 98 are attached to the respective seal grooves. This thrust member 9
Is mounted on the bottom surface of the frame 4, and a thrust back space 73 is formed on the back surface. Here, since the thrust member 9 may be rotated around the axial direction, a rotation stopper is unnecessary,
The structure of the compressor is simple and the workability is improved. further,
Since parallel movement within the plane of the swivel motion is also allowed, the gap between the side surfaces of the thrust member 9 can be set large until the sealability can be secured by the seals 97 and 98, so that the workability is improved. The discharge gas flows into the thrust rear surface space 73 from the pressure introducing hole 4u, and the discharge pressure becomes almost the same. This gives an approaching force that pushes the thrust member 9 upward. By this approaching force, the non-orbiting reference surface facing surface 7f of the thrust member 9 is pressed against the non-orbiting reference surface 2u on the same plane as the scroll wrap tooth tip of the non-orbiting scroll member 2 during normal operation. Here, since the scroll wrap addendum of the non-orbiting scroll member 2 and the non-orbiting reference surface 2u are on the same plane,
It is possible to easily manage the clearance between the tip and the bottom of the scroll wrap, and it is possible to provide a scroll fluid machine with small variations in performance and reliability during mass production. Further, when the scroll member is deformed during operation and pressure is applied between the tooth tops of the wraps, the thrust member 9 moves downward, so that the pressure contact between the tooth tops of the wraps is avoided, and compression is performed. The reliability of the machine can be secured. Here, an elastic body such as a leaf spring or heat resistant rubber may be arranged in the support back chamber 73. As a result, even if the discharge pressure is very low and the thrust member 9 cannot be pushed up only by the gas pressure in the support rear chamber 73, the thrust member 9 can be pushed up by its elastic force, so that the high efficiency of the compressor is achieved. The driving range can be widened.

Next, a fourth embodiment of the present invention will be described with reference to FIG. 22, which is a longitudinal sectional view. Here, an oil receiver 70 is provided, the pressure introducing hole that was a gas passage is used as an oil guide passage 4u that mainly serves as an oil passage, and either or both of the seal groove 9e and the seal groove 9d are removed. Seal 9
Since the seventh embodiment is the same as the third embodiment except that the parts 7 and 98 are also removed and the gap therebetween is reduced, the description of the configuration and operation of the other parts will be omitted. Since the discharge gas flowing through the flow passage 4h contains a large amount of lubricating oil, a part of the oil in the discharge gas is collected in the oil receiver 70. The pressure in the thrust rear space 73 becomes lower than the discharge pressure due to the gap between the thrust member 9 and the side surface without the seal. Due to this pressure difference, the oil pan 7
Oil accumulated in 0 from the oil guide path 4u to the thrust rear space 73
Flows into. As a result, the thrust rear space 73 plays a role of a damper against vibration of the thrust member, so that a highly reliable and highly efficient operation range can be expanded. Here, when the seal 97 on the inner periphery of the side surface of the thrust member 9 is removed, the pressure in the rear chamber 11 rises slightly, so the orbiting scroll member 3
The force for pushing up is increased, the sliding loss in the sliding thrust bearing 9a can be reduced, and the compression performance is improved. Further, the lubricating oil that lubricates the slide thrust bearing 9a contains the oil that has passed through the thrust rear space 73, and as a result, the temperature of the oil decreases,
Withstand load increases and reliability improves.

Next, a fifth embodiment will be described with reference to FIG. 23 which is a vertical sectional view. This is the main bearing 4
w and the lower main bearing 4a are divided and a groove is formed between them, and the lateral oil supply hole 12b is opened at this position, and an oil guide passage 4u is provided between this groove and the thrust rear space 73. Since this is the same as the embodiment, the description of the configuration and operation of other parts will be omitted. The oil discharged from the horizontal oil supply hole 12b is
It enters the thrust rear surface space 73 through the oil guide passage 4u. As a result, it is possible to provide a damper for the axial movement of the thrust member, and it is possible to widen the operating range of high reliability and high efficiency.

Next, a sixth embodiment will be described with reference to FIG. 24 which is a longitudinal sectional view. This is the same as the fifth embodiment except that the seals on the side surfaces of the thrust member are provided on both sides, and the discharge hole 4v that connects the thrust back space and the motor chamber is provided. Therefore, the description of the configuration and operation of the other parts will be omitted.
The oil discharged from the lateral oil supply hole 12b is transferred to the oil guide passage 4 by centrifugal force.
Enter the thrust back space 73 through u. The gas that has entered the thrust rear surface space 73 before operation is discharged to the motor chamber 92 through the discharge holes 4v. As a result, even if there is a seal on both sides of the thrust member, oil can be introduced into the thrust back space 73, so that a damper for axial movement of the thrust member can be provided while preventing leakage of discharge gas into the suction chamber 60. As a result, it is possible to provide a compressor having high reliability, volume efficiency, and further improved compression performance.

Next, a seventh embodiment in which the present invention is applied to a horizontal type thrust-float scroll compressor will be described with reference to FIG. 25 which is a longitudinal sectional view and FIG. 26 which is a plan view of a bearing support portion. . This is the same as the fourth embodiment except for the mechanism for storing the lubricating oil and the mechanism for supplying the lubricating oil to the main bearing and the thrust back space, and the description of the configuration and operation of the other parts is omitted.

A bearing support 18 having a vent hole 18b and a vent lid 18e in the upper part, an oil guide hole 18a and an oil guide cover 18d in the lower part, and a bearing hole 18c in the center is fixed to the cylindrical casing 1. , The oil storage chamber 80 is formed. Further, the discharge pipe 55 is taken out from the oil storage chamber 80. In addition, the bearing hole 18
The bearing housing 70 having the stationary oil supply pipe 71 fixed thereto is press-fitted into c. Further, the oil guide passage 4u is opened in the lower flow passage 4h. There is lubricating oil 56 in the opening of the oil guide passage 4u on the side of the flow passage 4h for horizontal installation. As a result, the thrust back space 7
No special mechanism is required to introduce the oil into No. 3, and the workability is improved. Compressed gas in the motor chamber 62 is ventilated lid 18
While colliding with e, it passes through the ventilation hole 18b and flows into the oil storage chamber 80. As a result, the pressure in the motor chamber 62 becomes
Since the pressure is higher than the pressure of 0, the lubricating oil 56 in the motor chamber 62 flows into the oil storage chamber 80 through the oil guide hole 18a. At this time, the gas also flows into the oil storage chamber 80 at the same time,
Although the bubbles rise in the lubricating oil inside, the bubbles rise along the bearing support portion 18 due to the oil guide lid 18d, so that the oil holes 7
Bubbles can be prevented from entering 1a, and reliability can be improved. As described above, the lubricating oil 56 can be stored inside the compact compressor without the oil surface of the motor chamber 62 contacting the rotor 15 and the shaft 12, so that a highly reliable horizontal compressor can be realized in a compact size. it can. The lubricating oil 56 lubricates the auxiliary bearing 72 through the stationary oil supply pipe 71 and flows into the oil supply hole 12a. Therefore, a highly reliable horizontal compressor can be realized in a small size.

[0070]

According to the present invention, it is possible to provide a fluid machine having high reliability, compression efficiency and workability, and having small variations in reliability and compression efficiency during mass production. Further, it is possible to provide a fluid machine having a simple structure, high assemblability and workability, and small variations in reliability and compression efficiency during mass production. Further, it is possible to provide a fluid machine having a wide operating range and a simple structure.

[Brief description of drawings]

FIG. 1 is a vertical sectional view of a first embodiment.

FIG. 2 is an explanatory diagram of a wrap width of a general scroll wrap.

FIG. 3 is a perspective view from above of the orbiting scroll member of the first embodiment.

FIG. 4 is a perspective view from below of the orbiting scroll member of the first embodiment.

FIG. 5 is a perspective view from below of the non-orbiting scroll member of the first embodiment.

FIG. 6 is a perspective view from above of the non-orbiting scroll member of the first embodiment.

FIG. 7 is a plan view of the bottom surface of the non-orbiting scroll member of the first embodiment.

FIG. 8 is a top view of the orbiting scroll member according to the first embodiment.

9 is a cross-sectional view taken along the line AA of FIG.

FIG. 10 is a perspective view from above of the Oldham ring of the first embodiment.

FIG. 11 is a perspective view from above of the stopper member of the first embodiment.

FIG. 12 is a top view of the stopper member according to the first embodiment.

FIG. 13 is an explanatory diagram of an oil groove position of the first embodiment.

FIG. 14 is a top view of the non-orbiting scroll member according to the first embodiment.

FIG. 15 is a sectional view of a stopper member of a second conventional example.

FIG. 16 is a vertical sectional view of a stopper member of a second conventional example.

FIG. 17 is a vertical cross-sectional view of the second embodiment.

FIG. 18 is a perspective view from above of the orbiting scroll member of the second embodiment.

FIG. 19 is a perspective view from below of the orbiting scroll member of the second embodiment.

FIG. 20 is a perspective view from above of the Oldham ring of the second embodiment.

FIG. 21 is a longitudinal sectional view of the third embodiment.

FIG. 22 is a vertical cross-sectional view of the fourth embodiment.

FIG. 23 is a vertical cross-sectional view of the fifth embodiment.

FIG. 24 is a vertical cross-sectional view of the sixth embodiment.

FIG. 25 is a vertical cross-sectional view of the seventh embodiment.

FIG. 26 is a plan view of the bearing support portion of the seventh embodiment.

[Explanation of symbols]

2 ... Non-orbiting scroll member, 2u ... Non-orbiting reference plane, 3 ...
Orbiting scroll member, 3d ... Thrust surface, 7 ... Stopper member, 7f ... Non-orbiting reference surface facing surface, 7g ... Thrust reference surface facing surface, 7i ... Scroll lap insertion hole, 7h ... Overhang portion, 9 ... Thrust member, 9b ... Thrust reference surface, 9a ... Thrust bearing, 8 ... Float rail member.

 ─────────────────────────────────────────────────── ─── Continuation of the front page (72) Hirokatsu Kosogabe, 502, Jinritsucho, Tsuchiura-shi, Ibaraki Prefecture, Hiritsu Seisakusho Co., Ltd. (72) Kazuya Matsuo, 502, Jinritsucho, Tsuchiura-shi, Ibaraki, Japan Tate Seisakusho Mechanical Research Center

Claims (9)

[Claims] 1. An orbiting scroll member which makes an orbiting motion with respect to a casing without rotation, an end plate, and a scroll wrap standing upright on the end plate. From a pump unit that forms a compression chamber by engaging a non-orbiting scroll member that is capable of parallel movement but almost all rotational movements in parallel with other directions, and a drive unit that realizes the orbiting movement of the orbiting scroll member. A thrust member that forms a thrust bearing facing the orbiting rear surface of the orbiting scroll member where the scroll wrap is not erected by the end plate and is fixedly arranged with respect to the casing; and the non-orbiting scroll member in the axial direction. An approaching force for approaching the thrust member and a minimum distance between the non-orbiting scroll member and the thrust member in the axial direction. In the scroll fluid machine having a distance defining mechanism for defining the above, the distance defining mechanism is provided with a non-orbiting reference surface in the same direction as the root of the scroll wrap of the non-orbiting scroll member in the non-orbiting scroll member, and the thrust is provided. In the member, a thrust reference surface on the thrust bearing side is provided at a position separated from the non-orbiting reference surface in a direction from the tooth bottom of the non-orbiting scroll toward the tooth tip by a distance larger than 0, and is fixedly arranged with respect to the casing. The stopper is sandwiched between the thrust reference surface and the non-orbiting reference surface, and the orbiting scroll member has an insertion hole of the scroll lap on the non-orbiting facing surface of the stopper member facing the non-orbiting reference surface. A scroll fluid machine characterized by being set to a size that cannot be passed through. 2. The scroll fluid according to claim 1, wherein the non-orbiting reference surface of the non-orbiting scroll member is set to be perpendicular to the axial direction, and the thrust reference surface of the thrust member is set to be perpendicular to the axial direction. machine. 3. The scroll fluid machine according to claim 2, wherein the non-orbiting reference surface and the tooth bottom surface of the scroll wrap of the non-orbiting scroll member are flush with each other. 4. The scroll fluid machine according to claim 2 or 3, wherein the thrust bearing of the thrust member is a slide bearing, and the slide bearing surface and the thrust reference surface are the same surface. 5. An orbiting scroll member that makes an orbiting motion with respect to the casing without rotation, an end plate, and a scroll wrap standing upright on the end plate, and in an axial direction perpendicular to the orbiting surface. From a pump unit that forms a compression chamber by engaging a non-orbiting scroll member that is capable of parallel movement but almost all rotational movements in parallel with other directions, and a drive unit that realizes the orbiting movement of the orbiting scroll member. And a thrust bearing that is formed by the end plate of the orbiting scroll member facing the orbiting back surface on which the scroll wrap is not erected and forms a thrust bearing, and is movable in the axial direction that is a direction perpendicular to the orbiting movement surface with respect to the casing. A member, an approaching force that causes the thrust member to approach the non-orbiting scroll member in the axial direction, and the non-orbiting scroll in the axial direction. In a scroll fluid machine having a distance defining mechanism that defines a minimum distance between a roll member and the thrust member, the distance defining mechanism has the same direction as the root of the scroll wrap of the non-orbiting scroll member in the non-orbiting scroll member. A non-turning reference surface is provided, a thrust reference surface on the thrust bearing side is provided on the thrust member, and a stopper member fixedly arranged with respect to the thrust member is provided between the thrust reference surface and the non-turning reference surface. A scroll fluid machine characterized by the above. 6. The scroll fluid machine according to claim 5, wherein the thrust member is integrated with the stopper member. 7. The scroll fluid machine according to claim 5, wherein the non-orbiting reference surface and the scroll wrap tooth bottom surface or tooth tip surface of the non-orbiting scroll member are the same surface. 8. An orbiting scroll member which makes an orbiting motion with respect to the casing without rotation, an end plate, and a scroll wrap standing upright on the end plate, and in an axial direction perpendicular to the orbiting surface. From a pump unit that forms a compression chamber by engaging a non-orbiting scroll member that is capable of parallel movement but almost all rotational movements in parallel with other directions, and a drive unit that realizes the orbiting movement of the orbiting scroll member. And a thrust bearing that is formed by the end plate of the orbiting scroll member facing the orbiting back surface on which the scroll wrap is not erected and forms a thrust bearing, and is movable in the axial direction that is a direction perpendicular to the orbiting movement surface with respect to the casing. A member, an approaching force that causes the thrust member to approach the non-orbiting scroll member in the axial direction, and the non-orbiting scroll in the axial direction. In a scroll fluid machine having a distance defining mechanism that defines a minimum distance between a roll member and the thrust member, a thrust back space that is a space that is slightly closed to the outside but is a substantially closed space on the side opposite to the thrust bearing of the thrust member. The scroll fluid machine is characterized in that an approaching force is provided by introducing oil having a pressure higher than the suction pressure therein. 9. The scroll fluid machine according to claim 8, wherein the scroll compressor is a horizontal type.