JPH11173283A - Intermediate pressure regulating valve for scroll machine - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide an intermediate pressure regulating valve which keeps sealing combination between turning and fixing scroll members constant and adequate even under variable operating condition in a scroll compressor. SOLUTION: In this compressor, fixing and turning involute laps 26 and 28 project from substantially flat and parallel arranged first and second surfaces 38, 40 of fixing and turning scroll members 22, 24 toward mating members, respectively, and are adjusted to engage with each other, and relative turning of both scroll members compresses fluid between both involute lap elements. A pressure regulating valve 90 which connects an intermediate pressure chamber 88, whose part is limited by a third surface 76 on the opposite side of the second surface of the turning scroll members, with delivery pressure chambers 52, 53 at a first position, and with a suction pressure chamber 54 at a second position, and is started by pressure difference between these chamber is provided in the scroll compressor, and both scroll members are held in the condition that they are closely combined axially.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention generally relates to a scroll compressor including a fixed scroll member and an orbiting scroll member, and more particularly, to a scroll compressor fixed to an orbiting scroll member by adjusting an intermediate pressure between a suction pressure and a discharge pressure. The invention relates to a valve that maintains an axial sealing connection with a scroll member.

[0002]

BACKGROUND OF THE INVENTION A typical scroll compressor is comprised of two facing scroll members, each having an involute trap, each wrap of which interlocks to define a plurality of closed compression pockets. As one of the scroll members pivots with respect to the other member, the pockets decrease in volume as they move between the radial outer and inner inlets. The pockets thus carry and compress the fluid contained therein, typically a coolant.

During operation of the compressor, the pressure of the compressed coolant tends to separate the scroll members axially. As the scroll members separate axially, the closure pocket leaks at the interface between the wrap tip of one scroll member and the surface of the other scroll member.
These leaks reduce the operating efficiency of the compressor,
In extreme cases, it can render the compressor inoperable.

[0004] Various axial compliance mechanisms have been developed as a result of the aforementioned efforts to minimize the leakage against the separating forces applied to the scroll members during operation of the compressor. For example, it is known to axially preload both scroll members with a force sufficient to oppose the dynamic separation force. Another method is to provide a thrust bearing interface between the fixed scroll member and the orbiting scroll member while guaranteeing minute manufacturing tolerances of the components, and to transmit an axial force between the two members. The most common method is to feed back the compressed refrigerant gas to drive the two scroll members together.

In general, the axial compliance force deflects the tip of the scroll compressor wrap against the inner surface of the opposite scroll and / or deflects the sliding surfaces on the outer peripheries of the two scroll members to engage each other. Can be matched. In such a contact area, a frictional force is generated as the movable scroll orbits around the fixed scroll. If excessive frictional force is generated by the axial compliance mechanism, the force required to operate the scroll compressor increases, and a mating surface may have a polishing effect. When the axial compliance force is generated by the surfaces of both scrolls, the polishing effect generated by the axial compliance force impairs the lap tip and inner surface or surface of both scrolls,
Alternatively, the wrap tip may be excessively worn, which adversely affects the sealing performance and long life of the wrap tip.

[0006] Some prior art scroll compressors have a passage in the orbiting scroll member,
Part of the compression chamber formed by scroll wraps interlocking with intermediate pressure containing coolant,
Through this passage, fluid is in direct communication with an intermediate pressure chamber, which is formed in part by the side of the orbiting scroll member on which the scroll wrap is not discharged. Refrigerant gas in the intermediate pressure chamber exerts an axial sealing force between the orbiting scroll member and the stationary scroll member. However, depending on the operating conditions, such an arrangement may generate an intermediate pressure exceeding the discharge pressure at the time of starting the compressor or the like, and the fixed scroll member and the orbiting scroll member are tightly adhered to each other, thereby disabling the efficiency of the compressor. . Conversely, if the intake pressure is low and the intermediate pressure is low, such an arrangement may not provide sufficient axial intermediate sealing force between the fixed scroll member and the orbiting scroll member. There is a need for a method of adjusting the intermediate pressure that deflects the fixed scroll member and the orbiting scroll member to keep the hermetic coupling constant and appropriate even when the operating conditions of the compressor change.

[0007]

SUMMARY OF THE INVENTION The present invention provides an intermediate pressure regulating valve which adjusts an intermediate pressure to deflect a orbiting scroll member to provide a constant and proper hermetic connection with a fixed scroll member even under variable operating conditions. provide. When the intermediate pressure is adjusted by the valve according to the present invention, the loss of frictional force is reduced, and the tips and inner surfaces of the fixed scroll member and the orbiting scroll member are held at a constant relative position in the axial direction.

The present invention comprises a stationary scroll member having a suction pressure chamber and a discharge pressure chamber, having a stationary involute trap element protruding from a substantially planar first surface, a substantially planar second surface and a substantially planar surface. An orbiting scroll member having an orbiting involute trap element protruding from a substantially planar third surface opposite to and substantially parallel to the planar second surface. The fixed scroll member and the orbiting scroll member are adapted to mesh with the fixed involute trap element projecting toward the second surface and the orbiting involute trap element projecting toward the first surface. Since the first surface and the second surface are arranged substantially parallel, the relative rotation by the scroll members compresses the fluid between the involute trap elements. An intermediate pressure chamber, partially defined by a substantially flat third surface of the orbiting scroll member, is connected to a discharge pressure chamber at one valve position and a suction pressure chamber at another valve position through a spring bias valve. Fluid is communicating. Alternatively, fluid adjusted to an intermediate pressure can flow through a fixed scroll that is supported for limited axial movement. With such a device, the axial sealing connection between the fixed scroll member and the orbiting scroll member is properly maintained by the fluid pressure induced forces in the intermediate pressure chamber.

An advantage of the present invention is that the intermediate pressure is adjusted by using the intermediate pressure regulating valve, so that an excessive axial compliance force is not applied to the wrap tip and the fixed position is maintained with respect to the scroll surface on the opposite side. Is to be able to. Therefore, the wear of the lap tip is small.

[0010]

BRIEF DESCRIPTION OF THE DRAWINGS The above and other features and objects of the present invention, and the manner of achieving it, are as described in the following description of embodiments of the invention taken in conjunction with the accompanying drawings. The invention will become clearer and the invention itself will be better understood.

[0011] Throughout the drawings, corresponding reference numerals indicate corresponding parts. The drawings showing the embodiments of the present invention are not necessarily drawn to scale, and there are places where features are emphasized. Although the illustrations set forth herein illustrate embodiments of the invention in some form, the examples disclosed below, although exhaustive, have been disclosed by the following detailed description of the invention. It should not be construed as limiting the invention to any particular form, nor should it be construed as limiting the scope of the invention in any manner.

Referring to the drawings, and more particularly to FIGS. 1 and 2, a motor 13 having a housing 12, a stator 14 and a rotor 15, a crankshaft 36 on which the rotor 15 of the motor 13 is mounted, and a lower portion of the housing 12. An outer bearing assembly 16 axially supporting the end of a shaft 36 and an oil pump 18 for moving oil from a sump 19 located at the bottom of the housing 12 to lubricate compressor components. The illustrated scroll compressor 10 is shown. Scroll compressor 10
Further includes a fixed scroll member 22 and an orbiting scroll member 24. The fixed scroll member 22 and the orbiting scroll member 24 each have a spiral scroll element or wrap, 26 and 28. The scroll wraps 26, 28 mesh with each other and are used to compress gas in a known manner by orbiting the orbiting scroll member 24 relative to the fixed scroll member 22. Scroll compressors are well known to those skilled in the art and are described herein in U.S. Pat. Nos. 5,131,828 and 5, assigned to the assignee of the present invention, which disclose the structure and operation of scroll compressors. , 38
No. 3,772 is incorporated for reference. In general, the coolant flows at low pressure from the suction pipe 55 into the suction pressure chamber 54, where the intermeshing scroll wraps 26, 28
Between the two scroll wraps and through the discharge port 51 in the fixed scroll member 22 and located at the uppermost part of the housing 12. It is discharged to the discharge pressure chamber 52. First discharge pressure chamber 52 and second discharge pressure chamber 53 located below housing 12
Means that the fluid moves through the passage 42. Passageway 42
The inner wall of the housing 12 extends between the fixed scroll member 22 and the frame 20. The fixed scroll member 22 and the frame 20 are connected to each other by, for example, a plurality of bolts 23. The high pressure fluid exits the compressor 10 through a discharge pipe 56 that is open to a second discharge pressure chamber 53.

The orbiting scroll member 24 includes a hanging bearing base 30, which is mounted on a roller 32 via an intermediate bearing 34. The end of the roller 32 is supported or fixed to an eccentric crankpin 35 of a crankshaft 36. The rotation restricting means such as the Oldham coupling ring 50 or the like disposed between the fixed scroll member 22 and the orbiting scroll member 24 includes the orbiting scroll
It is used to prevent free rotation about a unique axis when turning about the axis.

In the embodiment shown, oil is carried from the sump 19 under discharge pressure through a passage 44 in the crankshaft 36 and exits through an opening 46 at the top end of the crankpin 35 to provide a bearing. Lubricate the interface between the roller and the roller and the crankpin. Journal bearings (not shown) may also be lubricated. The oil coming out of the bottom of the bearing 34 returns to the oil reservoir 19 through the passage 21 in the frame 20. Alternatively, the passage 44 and the roller 3
A lubricating oil may be supplied directly to the bearing 34 using a radial passage (not shown) extending between the outer surface of the bearing 34 and the outer surface of the bearing 34. In this case, the passage 44 is formed without supplying the opening 46 to the top end of the crankpin 35. In either of these two embodiments, the oil also passes through an orifice 48 located within the orbiting scroll member 24 and from the portion between the orbiting scroll member 24 and the roller 32 to between the scroll wraps 26 and 28. Supplied to the area. The pressure in the region between the scroll wraps 26, 28 is set at the discharge pressure chambers 52, 5 during normal compressor operation.
3 and midway between the pressures experienced in the suction pressure chamber 54. By introducing oil into the region between the scroll wraps 26 and 28, the sliding surface between the two and the wraps 26 and 28
Lubrication is provided to the sliding surfaces between the inner surfaces 38, 40 of each of the fixed and orbiting scroll members, each of which protrudes, and the lap tip slidably mounted thereon. The lubrication of the sliding surface is controlled by the orbiting scroll 24
Since the frictional resistance generated during the operation of the scroll compressor 10 is reduced, the output loss due to the friction during the operation of the scroll compressor 10 is reduced, and the useful life of the sliding surface is extended.

As the orbiting scroll member 24 moves,
Fluid, such as refrigerant gas, is compressed between the scroll wraps 26, 28 to create a separating force. The separating force acts on the inner surfaces 38, 40 of the fixed and orbiting scroll members. The force generated by the compressed fluid is two scrolls 22, 24
In the axial direction. Using the present invention, it is possible to deflect the orbiting scroll 24 in the direction of the fixed scroll 22 while the compressor is operating, the axial separation force is suppressed, and the scrolls 22, 24 are deflected and joined to each other. .

As shown in FIG. 1, the scroll compressor 10 has a frame 20.
It includes a main bearing portion 58 that radially supports the crankshaft 36 through a journal bearing 57. As best seen in FIG. 2, the recessed portion of the frame 20 adjacent above the main bearing portion 58 receives the bearing pedestal portion 30 of the orbiting scroll member and has a substantially flat frame surface 60 and a generally cylindrical wall. 62. The substantially flat bottom surface 64 of the orbiting scroll bearing base portion 30 is positioned parallel to the frame surface 60 and has an annular seal groove 66 and associated seal 68 therein. The size and material of the seal 68 are the same as those of the orbiting scroll member 24.
When pivoting relative to the frame 20, it slidably engages the frame surface 60 and deflects its axial position toward the fixed scroll member 22 in response to axial compliance means described below. belongs to. Therefore, referring to FIGS. 3 and 4, the seal 6
It can be seen that 8 is a boundary between 70 and 72, inside and outside the bottom surface of the bearing base.

The outer surface of the bearing pedestal portion 30 may have a large annular groove 74 therein. Orbiting scroll member 24
Also, a substantially flat bottom surface 7 adjacent the bearing stand portion 30
6 is included. The bottom surface 76 is substantially parallel to the orbiting scroll surface 40. Surface 76 is disposed parallel to flat frame surface 78 and is substantially vertically adjacent to frame wall 62, which is generally cylindrical. Surface 76 has an annular seal groove 80 and its associated seal 82 therein.
And The size and material of the seal 82 is such that when the orbiting scroll member 24 orbits relative to the frame 20, it engages with the frame surface 78 in a slidable manner;
It is of a kind that deflects its axial position toward the fixed scroll member 22 in response to an axial compliance means described later. Accordingly, the seal 82 is a boundary between the inside and outside of the bottom surface and each of 84 and 86.

The above arrangement includes the seals 68 and 82, the generally cylindrical frame wall 62, the outer surface of the orbiting scroll member's bearing stand portion 30, the inner bottom surface 84 of the orbiting scroll member, and the flat frame below. Surface part 78
, And an intermediate pressure chamber 88 defined by the bearing pedestal outer bottom surface 72 and the flat frame surface 60 therebelow. During normal compressor operation, the pressure chamber 88
The fluid is arranged at a pressure between the suction pressure and the discharge pressure as described in detail below. The area outside the seal 82 is in fluid communication with the suction pressure chamber 54, and thus with the outer bottom surface 86, and the portion of the frame 20 below is under suction pressure during operation of the compressor. The area inside the seal 68, which is partially limited by the bearing base inner bottom surface 70 and the inner surface of the bearing base part 30, is connected to the second discharge pressure chamber 53 through the passages 21 and 44. Overflowing with oil. Therefore, in this latter region, the discharge pressure is applied during the operation of the compressor. The axial forces generated by the respective pressures on surfaces 86 and 70 and the surface of orbiting scroll member 24 adjacent on rollers 32 and crankpin 35 create an inner bottom surface 84 of the orbiting scroll member and a bearing base outer bottom surface 72. Combined with the two axial intermediate pressures exerted on it, apply a total compliance force in the axial direction, which overwhelms the axial scroll separation force that occurs during compression. The net axial compliance force that ensures a sliding hermetic connection between the wraps 26, 28 and the scroll surfaces 40, 38, respectively, is the difference between the total axial compliance force and the axial scroll separation force.

The intermediate pressure regulating valve assembly 90 generally includes a valve body 92, a valve piston 94, a compression spring 96,
It can be made of steel. The valve body 92 and the valve piston 94 are made of sintered powder metal, cast iron,
It can be produced by machining steel or aluminum, or by injection molding of thermoset plastic. As shown in FIGS. 3 and 4, the valve body 92 has a slightly cylindrical hollow, but a part of its outer surface may be rectangular (not shown), and the inside of the frame 20 is generally reduced. The one end of the valve body 92 is opened to the intermediate pressure chamber 88, and the other end of the valve body 92 is adapted to fit into the receiving hole formed in the radial direction by an interference fit or the like. It is open to 53. Frame 20
Discharge gas passage 9 extending through and one side of valve body 92
8 indicates that fluid is discharged from the second discharge pressure chamber 53 to the intermediate pressure chamber 88 while the valve assembly 90 is operating.
It works to supply to. The suction gas passage 101 is located radially outward from the discharge gas passage 98 along the valve body 92, extends through one side of the valve body 92, and extends from the frame 20.
To the passage 132 in the inside. During operation of valve assembly 90, passages 101 and 132 serve to pump intermediate pressure fluid from intermediate pressure chamber 88 to suction pressure chamber 54. Intermediate pressure fluid in the chamber 88 is provided by an inner bottom surface 84 of the orbiting scroll member and a bearing base outer bottom surface 72.
Acts on the area defined by the inside of the seal groove 80 and the area outside of the seal 68 to generate a part of the axial compliance force to cause the axial separation of the scroll members 22 and 24 occurring during operation of the compressor. Oppose. How the fluid moves between the chambers 53, 88 and 54 through the valve assembly 90 will now be described.

The valve body 92 includes an inwardly projecting annular stop 114 near its radially outer end. In the embodiment shown in FIGS. 1-4, a compression spring 96 is disposed within the valve body 92 with one end thereof contacting the annular surface 115 of the stop 114. Referring now to FIGS. 5-7, a generally cylindrical valve piston 94 is provided with a longitudinal bore 1.
It comprises a tubular portion 102 having a free end region 128 and a shaft portion 106 having a free end region 130. The free end region 128 of the barrel portion includes the barrel portion 10 exposed to the intermediate pressure chamber 88, including the diameter region of the bore 104.
2 encompasses the entire end face region. The diameter of the shaft portion 106 is clearly smaller than the outer diameter of the cylindrical portion 102 and the joint of the coaxial portions 102 and 106 has an annular shoulder 116.
There is. The outer surface 108 of the tube portion has an annular groove 124 near the junction of the shaft portion 106 and the tube portion 102. The port 126 extends radially through the cylindrical wall of the piston 94, allowing fluid to communicate with the annular groove 124 and the longitudinal hole 104.

As shown in FIGS. 3 and 4, the valve piston 9
4 is received in the valve body 92 and the cylindrical portion 10 of the valve piston
The second outer surface 108 is slidably coupled to the inner surface 110 of the valve body 92. Shaft portion 106 extends along the center of spring 96 and annular valve body stop 114, and spring 96
The end opposite to the stop 114 is in contact with the shoulder 116. The valve assembly 90 is equipped with a seal 118, which may be neoprene rubber, to seal off the ingress of discharge gas that the shaft portion 106 of the piston and the stop 114 of the valve body leak.
The shaft portion 106 is slidably connected to the side of the valve body stop 114 opposite to the spring receiving surface 115 through the seal 118. An annular end plug 120, which can be manufactured by sintering of powder metal, machining of cast iron, steel or aluminum or injection molding of plastic, has a cylindrical cavity 122 at the radially outer end of the valve body 92. Tightly holding the seal 118. The end plug 120 can be held in place within the cavity 122 by an interference fit or by appropriately staking a portion of the valve body material. Shaft portion 106 moves as piston 94 rapidly moves radially outward within valve body 92 during operation of the compressor.
The end plug 120 extends out of the valve body 92 from an opening at the center. The valve body 92 may be equipped with a snap ring 112 in a receiving phase groove 113 near its radially inner end to limit radially inward movement by the valve piston 94. Suction pressure chamber 99 having an annular cross section
Are the inner surface 110 of the valve body 92 and the shaft portion 1 of the valve piston.
The outer surface 107 of FIG. 6 (FIG. 5), the annular shoulder 116 of the valve piston 94 (FIG. 5) and the surface 115 of the stop 114 of the valve body. The suction chamber 99
A passage 132 in the frame 20 and at least one of the two passages 100, 101 extending radially through the valve body 92 connect to the suction chamber 54. The passage 100 is outside the passage 101 along the valve body 92, and both passages 1
00 and 101 both extend into passage 132.

Prior to starting the compressor 10, a refrigeration system (not shown) comprising the compressor 10, a coolant system, a heat exchanger, and a receiver, if any, is provided.
Through, the pressure is equalized. Because the free end region 130 of the valve piston shaft and the annular shoulder 116 of the valve piston mate to match the free end region 128 (FIGS. 5 and 7) of the tubular portion of the valve piston, such an axial surface of the valve piston 94 is The acting equalized pressure creates an axial counterforce acting evenly on these surfaces. Therefore,
Pressure forces do not deflect the valve piston 94 to any end of the valve body 92. However, the compression spring 96 drives the valve piston 94 radially inward along the valve body 92 so that the annular groove 124
Is kept in communication with the discharge gas passage 98 in the inside. Thus, the intermediate pressure chamber 88 communicates with the second discharge pressure chamber 53 via the piston bore 104, the port 126, the annular groove 124, and the passage 98, as shown in FIG.

When the compressor is started, the discharge pressure chambers 52 and 53 and the intermediate pressure chamber 8 connected thereto are set.
The pressure of the fluid at 8
4 rises to a point that opposes the force exerted by the valve body stop 114 through the spring 96, and the valve piston 94 causes the valve body 92 to move to the point where the annular groove 124 no longer communicates with the passage 98. Move radially outward along. At this point, the intermediate pressure chamber 88 is sealed and not in communication with either the discharge pressure chambers 52, 53 or the suction pressure chamber 54.

If, during operation of the compressor, the discharge fluid pressure apparently drops so that the scroll members 22 and 24 become too tightly deflected with respect to each other, the valve piston 94 causes the intermediate pressure in the chamber 88 and the suction pressure in the chamber 99 to decrease. And the force induced by the combination of the now reduced discharge pressure in the discharge pressure chambers 52, 53 causes the valve body 92 to move radially outward against the force of the compression spring 96. 4 to the point where the annular groove 124 is connected to the passages 101, 132 to allow fluid to flow from the intermediate pressure chamber 88 to the suction pressure chamber 54. This reduces the pressure in chamber 88,
Scrolls 22 and 24 are no longer over-coupled to each other. Further, with the pressure drop in the chamber 88,
The combination of the spring force and the pressure-induced net force on the valve piston 94 causes the valve piston 94 to move radially inward, also along the valve body 92, thus causing the chamber 88 to move into the suction pressure chamber 54. I will not be able to communicate.

When the discharge pressure rises significantly during operation of the compressor and the drive scroll members 22, 24 are separated from their proper axial connection, the result is an increase on the free end region 130 of the shaft portion. The force, the suction pressure in the chamber 99, and the force of the spring combine to drive the piston 94 radially inward along the valve body 92 and into the annular groove 124.
Communicates with the passage 98 to increase the pressure in the chamber 88.
Thus, the orbiting scroll member 24 is more rigidly axially coupled to the fixed scroll member 22 to counter the increasing axial separation force.

If the suction pressure rises significantly during the operation of the compressor, the gas pressure between the scroll wraps 26, 28 will increase accordingly, and the drive scroll members 22, 24 will increase.
From its proper axial connection. However, the increase in suction pressure is caused by the suction passages 100, 101, 132.
Through the chamber 99 to drive the valve piston 94 radially inward along the valve body 92 so that the annular groove 124
Communicates with passage 98 to establish communication between intermediate pressure chamber 88 and discharge pressure chamber 53. Therefore, chamber 8
8, the orbiting scroll member 24 is more securely axially coupled to the fixed scroll member 22 to oppose the increasing axial separation force.

If the suction fluid pressure decreases significantly during operation of the compressor, the gas pressure between the scroll wraps 26, 28 will correspondingly decrease, leaving the scroll members 22 and 24 excessively deflected relative to each other. However, the reduction in suction pressure leads to chamber 99 by suction passages 100, 101, and 132, reducing the pressure-inducing force on valve piston shoulder 116, and as shown in FIG. Fluid can be drained from the intermediate pressure chamber 88 to the suction pressure chamber 54 to move radially outward along the valve body 92 to a position leading to 101, 132. The pressure in the chamber 88 is thus reduced, and the scrolls 22 and 24 are released from an overly rigid connection between each other. Further, as the pressure in chamber 88 decreases, the combination of the spring force and the net pressure-inducing force on valve piston 94 causes the piston to move radially inward along valve body 92 and chamber 88 No longer communicates with the suction pressure chamber 54.

In the above method, the intermediate pressure regulating valve and the intermediate pressure chamber provide a self-adjusting shaft compliance means for the scroll compressor. When actually reducing the intermediate pressure regulating valve of the present invention, the preload 1.
A compression spring 96 having a spring constant of 0.9 pounds per inch at 0 pounds, a free end area 128 of a 0.0491 square inch cylindrical section, and a free end area 130 of a 0.0123 square inch shaft section; It has been found that good results can be achieved with an annular shoulder 116 having an area of 0.0368 square inches. These parameters are merely illustrative of one embodiment of the present invention,
It should not be considered as limiting the scope of the invention. In particular, the compression spring 96 is not required for the practice of the present invention, and merely the valve assembly 90 is
It only serves to increase the speed at which the pressure in 8 is adjusted.

Although the present invention has been described as having an exemplary design, the present invention can be further modified within the spirit and scope of the present disclosure. This application is therefore intended to cover any variations, uses, or adaptations of the invention using its general principles. Further, this application is intended to cover such departures from the present disclosure as come within known or customary practice in the art to which this invention pertains. Accordingly, the scope of the invention should be determined not by the embodiments illustrated, but by the following claims and their legal equivalents.

[Brief description of the drawings]

FIG. 1 is a longitudinal sectional view of a scroll compressor including an embodiment of the present invention.

FIG. 2 is an enlarged partial sectional view of an upper portion of the scroll compressor shown in FIG.

FIG. 3 is an enlarged partial sectional view showing the valve mechanism according to the present invention in a position where a discharge pressure chamber and an intermediate pressure chamber are in fluid communication.

FIG. 4 is an enlarged partial cross-sectional view showing the valve mechanism according to the present invention in a position where the suction pressure chamber and the intermediate pressure chamber are in fluid communication.

FIG. 5 is a side view of a valve according to the present invention.

FIG. 6 is an end view of the valve shown in FIG. 5;

FIG. 7 is a longitudinal sectional view of the valve shown in FIGS. 5 and 6, taken along line 7-7 of FIG. 6;

Claims (10)

[Claims] 1. A scroll compressor having a suction pressure chamber and a discharge pressure chamber, a first scroll member having a first involution trap element protruding from a substantially flat first surface, and a second substantially flat member. A second scroll member having a second involute trap projecting from a surface and a third surface opposite the second surface, which is substantially flat, wherein the first and second scroll members are connected to each other by the first first and second scroll members; An involute trap element projects toward the second surface;
The scroll members are also adapted so that the second involute trap element is adapted to protrude and join toward the first surface, and wherein the first surface is disposed substantially parallel to the second surface. A second scroll member such that the relative rotation of the second scroll member compresses the liquid between the two involute trap elements; an intermediate pressure chamber partially defined by the third surface of the second scroll member; Communicates with the discharge pressure chamber at a first position and communicates with the suction pressure chamber at a second position, wherein the valve is connected to the intermediate pressure chamber, the discharge pressure chamber, and the suction pressure chamber. Actuated, whereby the first and second scroll members are guided by hydraulic pressure in the intermediate pressure chamber. Scroll compressors are held in a state of being coupled to sealing axially force. 2. The scroll compressor according to claim 1, wherein said intermediate pressure chamber does not communicate with any of a discharge pressure chamber and a suction pressure chamber when said valve is located between said first and second positions. 3. The valve of claim 1, further comprising a hollow valve body in which the valve is slidably disposed, wherein the interior of the valve body communicates with the intermediate pressure chamber and the interior of the valve body communicates with a discharge pressure chamber through a first conduit. And the inside of the valve body is
The scroll compressor according to claim 1, wherein the scroll compressor communicates with a suction pressure chamber through a conduit, and the intermediate pressure chamber is connected to the discharge pressure chamber and the suction pressure chamber through the first and second conduits, respectively. 4. A valve wherein said valve communicates with said intermediate pressure chamber and a passage which communicates said hole with said first and second conduits when said valve is located in said first and second positions, respectively. The scroll compressor according to claim 3, comprising: 5. The scroll of claim 3, further comprising a spring operably disposed between said valve and said valve body, said spring deflecting said valve toward said first position. compressor. 6. The scroll compressor according to claim 3, wherein said valve is generally cylindrical and said valve body interior is partially defined by a cylindrical surface. 7. The scroll compressor according to claim 3, wherein said valve is adapted to move linearly between said intermediate pressure chamber. 8. A valve according to claim 8, wherein said valve has a first surface area exposed to said intermediate pressure chamber, a second surface area exposed to a discharge pressure chamber, and a third surface area exposed to a suction pressure chamber.
The surface of claim 1, wherein the pressure applied to the first, second and third surface regions generates a force to move the valve between the first and second positions. Scroll compressor. 9. The scroll compressor according to claim 1, further comprising a spring, wherein said spring deflects said valve toward said first position. 10. A scroll compressor having a suction pressure chamber and a discharge pressure chamber, a first scroll member having a first involution trap element protruding from a substantially flat first surface, and a second substantially flat second scroll member. A second scroll member having a second involute trap projecting from a surface and a third surface opposite the second surface, which is substantially flat, wherein the first and second scroll members are connected to each other by the first first and second scroll members; An involute trap element projects toward the second surface;
The scroll members are also adapted so that the second involute trap element is adapted to protrude and join toward the first surface, and wherein the first surface is disposed substantially parallel to the second surface. A second scroll member such that the relative rotation of the second scroll member compresses the liquid between the two involute trap elements; an intermediate pressure chamber partially defined by the third surface of the second scroll member; Means for communicating the intermediate pressure chamber with one of the discharge pressure chamber and the suction pressure chamber in response to a pressure difference existing between the discharge pressure chamber and the suction pressure chamber; The first and second scroll members are axially hermetically coupled by a force induced by hydraulic pressure in the intermediate pressure chamber. Scroll compressors are held in a state.