JPH03548B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION Field of the Invention This invention relates to an improved valve arrangement for fluids, particularly suitable for use in gas compressors. The invention also relates to a valve device incorporating a capacity reduction mechanism for a gas compressor. However, the present invention relates to a valve device that can be used in both gas compressors with and without a capacity reduction mechanism.

Conventional technology and its problems No. 1 A typical reciprocating piston type gas compressor has a pressure-responsive suction and discharge valve mechanism built in between the head section and the compression chamber at the end of the cylinder. ing. Provide a port area that is large enough to allow the maximum volume of gas flow in a given time and under an acceptably small pressure drop in the overall operation of the gas compressor. It is important to. This is particularly important in refrigeration compressors used in air conditioning systems, since air conditioning systems generally require relatively large flow rates. In addition to the desire to maximize port area for a given cylinder size, the need to reduce the weight of the movable valve member and limit the inertial effects of the valve member also reduces the noise generated by the valve gear, especially in high speed compressors. It is advantageous to minimize the

It is also important in such gas compressors to minimize the re-expansion volume or clearance volume at the valve end of the cylinder. The valve and compression chamber walls should therefore have a shape that is complementary to the top of the piston so that the piston can minimize the volume of the compression chamber without restricting gas flow during its compression stroke. This requirement can be met by creating a composite piston head shape, but composite pistons are extremely expensive to manufacture and difficult to assemble, and also Throttling losses often occur. Reducing reexpansion volume is extremely important in relatively low flow rate refrigeration compressors, such as those employed in very low temperature refrigeration systems, and in heat pump applications.

Second, in many refrigeration systems (and heat pump devices), it is required to control or reduce the capacity of the gas compressor. The need for adjustment of compressor capacity allows the refrigeration system to function to balance the heat input load at the selected temperature for the evaporator in systems requiring variable heating and cooling. This occurs when a constant displacement pump is used. The capacity or load of the compressor is varied between a minimum value and a maximum value set in the refrigeration system.

Load balancing in gas compressors is commonly accomplished by thermal expansion valves that control the flow of liquid phase refrigerant into the evaporator. When the heat load decreases in the refrigeration system, the expansion valve reduces the refrigerant flow rate. Conversely, when the heat load increases, the expansion valve increases the refrigerant flow rate. Therefore, if the refrigeration system is not equipped with any capacity control means, the suction pressure will decrease due to a decrease in the refrigerant flow rate. Therefore, the capacity of the compressor is
It will be reduced when the compressor operates at a relatively high compression ratio and a relatively low volumetric efficiency. Such capacity reduction can be tolerated to a certain extent, and is usually considered when designing a refrigeration system.
taken into account. However, there is a minimum suction pressure or suction temperature at which the compressor or refrigeration system should not operate, such as the saturation suction temperature at which frost begins to form on the coils of an air-cooled evaporator or the minimum critical temperature of a water cooler. be.

In some cases, particularly in cryogenic refrigeration systems, the reduction in flow rate causes the compressor to overheat when the compression ratio becomes excessive. In relatively small refrigeration systems, simple means can be used to overcome these problems, such as using a thermostat or suction pressure responsive switch to turn the compressor on and off. However, when the refrigeration system is relatively large, the above solution is undesirable since it results in large temperature fluctuations and a negative impact on compressibility. Therefore, in large refrigeration systems, sensors are used to selectively activate a capacity reduction mechanism (unloader) for reducing the capacity of a compressor without interrupting operation of the compressor.

Several different types of unloaders have been used so far, including hot gas branch flow type unloaders, suction gas cutoff type unloaders, unloaders with a mechanism for raising the suction valve, and re-expansion type unloaders. There is an unloader with an additional gap.
In the type of unloader with a re-expansion gap added air gap, a gap separated from the cylinder by a stop valve or the like is utilized to provide additional re-expansion volume or re-expansion gap to reduce the volumetric efficiency of the compressor. Ru.

Conventional capacity reduction devices that utilize gap-added voids have several drawbacks. Such conventional devices are bulky and are not suitable for use in today's high speed compressors where compactness is an important design goal. Some conventional devices rely on artificial adjustment of a valve or piston to provide additional clearance volume. Although such prior art techniques have been utilized to control a relatively small number of low speed compressors, manual adjustments are impractical in today's air conditioning or refrigeration systems where automatic control is desired. In addition, the previous device was a compressor valve device developed by the applicant, as disclosed in U.S. Patent No. 4368755 dated January 18, 1983, which had excellent gas flow characteristics when the valve rose. The valve system achieves excellent sealing without permanent deformation, operates quietly and without noise, and is extremely suitable for high-speed compressors.
It has become impossible to incorporate it.

Problem of the Invention This invention first addresses the conventional technology and one of its problems in a gas compressor, regardless of whether a mechanism for reducing the capacity of the compressor is provided.
The present invention aims to provide a valve device that satisfies the various requirements mentioned above and is suitable for use as a discharge valve. That is, the main object of the present invention is to increase the efficiency of a gas compressor or similar fluid transport machine, improve the discharge flow characteristics during valve lift, and to improve the efficiency of a gas compressor or similar fluid transport machine without permanently deforming the valve member. It improves the sealing characteristics of valves, allows compressors to operate quietly and smoothly, and can be suitably used in high-speed compressors.
The purpose of the present invention is to provide a new valve device.

Another object of the present invention is to provide a valve device as described above, which may include an unloader of a type having an additional gap with a re-expansion gap, in relation to the second part of the prior art and its problems. An object of the present invention is to provide a novel valve device.

Structure and Effects of the Invention When the valve device according to the present invention includes an unloader, that is, a mechanism that can reduce the capacity of a gas compressor, an opening is formed in the valve for the gas compressor. A hole is formed in the head portion connected to the valve plate to provide a re-expansion gap. The plunger that is slidably fitted into the hole is provided with a rod that extends into a hollow cylindrical column disposed within the opening of the valve. The plunger described above is adapted to be moved to a first position which interrupts communication between the compression chamber of the compressor and the air gap and places the compressor in a fully loaded condition. Further, the plunger can be pulled out from the opening of the valve and moved to a second position where the compression chamber and the cavity are communicated with each other to reduce the load or capacity of the compressor.

When the valve device according to the present invention is embodied as a gas compressor equipped with a capacity reduction mechanism,
The above-described structure allows the discharge valve mechanism to form part of a capacity reduction mechanism for enlarging the gap volume, resulting in a compact device. The weight of the discharge valve is reduced, which reduces the impact on the valve seat when the valve closes. In a preferred embodiment, a retainer is provided that has a hollow column portion that serves to guide the valve during its movement and seating on the valve seat. A sealing means is provided between the valve and the columnar portion to enable the valve to be disposed on the columnar portion in a sealed and slidable manner, and to provide a cushioning effect to reduce the impact of the valve. will be placed in the

In another embodiment of the invention, a solenoid is used to quickly move the plunger to a non-reducing position or a reduced compressor capacity position. Capacity control is thus achieved automatically and without the need for human adjustment. In another embodiment, a sizable insert or sleeve is inserted into the head hole to determine the amount of retraction of the plunger and to adjust the clearance volume added by the void to the desired degree of volume reduction. They can be inserted alternately as needed.

The invention is inexpensive, simple, operates with high efficiency in gas compressors and other fluid transport machinery, and
The present invention provides a valve device that has all the advantages of the valve device disclosed in the aforementioned US Pat. No. 4,368,755. In other words, this invention reduces the friction between the columnar body and the valve as described above in fluid transport machines such as gas compressors, and operates smoothly at high speed. To provide a valve device having excellent sealing properties for sealing between valves.

This advantage is achieved by forming an opening therethrough in a valve movable between a closed position and an open position, and having a columnar body fixed in position fit and supported in the opening, whereby the columnar body allows the valve to be moved between a closed position and an open position. is slidably guided between an open position and a closed position, and a sealing member is provided to prevent fluid flow between the valve and the columnar body when the valve is in the closed position. ,Given.

In one embodiment of the present invention, the above-described sealing member is provided as follows. That is, the valve is provided with a shoulder portion having a sealing surface at a portion outwardly distanced from the opening, and the columnar body is also provided with a shoulder portion having a sealing surface. The elastic sealing member is disposed so as to sealingly engage with both the sealing surface of the valve and the sealing surface of the columnar body when the valve is in the closed position. Prevent fluid leakage between the Such a sealing member is capable of elastically deflecting while the valve slides between the open and closed positions and does not slide against the columnar body. The sealing member is biased by the pressure difference between the gas pressures acting on both sides of the valve into sealing engagement with the sealing faces when the valve is in the closed position; It is desirable that a spring biasing the member in the above direction be compressed between the sealing member and the valve device fixing portion.

In a preferred embodiment of the invention, the valve arrangement described above is utilized as a discharge valve arrangement for a reciprocating piston gas compressor. In this embodiment, the valve arrangement comprises a valve plate having a through opening defining a valve seat, with which the valve engages sealingly in its closed position. Preferably, the valve and said post have a flat end face at the end opposite said shoulder, and the end face of said valve and post and the inner end face of the valve plate are mutually aligned when the valve is in the closed position. are assumed to be located on the same plane. In this way, the two end surfaces and the inner end surface, which are located on the same plane in the valve closed position, are at the end of the compression chamber of the compressor, and the re-expansion volume in the compression chamber is not expanded and the volume is minimized. This is advantageous when the capacity is not reduced and when no mechanism is provided to perform the same reduction.

Embodiment FIGS. 1-13 illustrate an example in which the embodiment of the valve device according to the present invention is used in a gas compressor. As will be understood from the following explanation, the valve device according to the present invention is It can also be used in other fluid transport machines other than compressors or heat pumps.

1-3, a valve assembly with an unloader mechanism, designated generally by the reference numeral 10, is shown together with a reciprocating gas compressor. The compressor body 12, which is a cylinder block, is provided with a cylinder bore 14 for receiving a reciprocating piston 16 having a seal ring 18, and has a suction space 20 adjacent to the cylinder bore 14.
The suction space 20 communicates in a known manner with the inlet of the gas to be compressed, which gas is usually fed from an evaporator in the refrigeration system.

Valve plate 22 has a plurality of suction passages 24 , 26 communicating with suction space 20 . An annular valve seat 28 that expands outward is provided at the center of the valve plate 22, and an opening in the valve seat 28 forms a part of the discharge passage. A typical reed-type suction valve has portions 30 and 32 located opposite to the suction passages 24 and 26 that are connected to each other to perform a valve function.

The discharge port 34 penetrates the valve plate 22 and
It is divided by 8. A pressure-responsive valve 36 is disposed within the discharge port 34, and the lower end portion of the valve 36 has a frusto-conical shape and is capable of sealingly engaging the valve seat 28. Pressure responsive valve 3
6 is energized by suction pressure during the suction stroke of the piston 16 to sealingly engage the valve seat 28, and the valve 36 is energized by the suction pressure during the suction stroke of the piston 16, and engages in a sealing manner with the valve seat 28 via a protective shim 41.
It is urged to move in the direction of engagement with the valve seat 28 by a disc spring 40 acting on the valve seat 28. During the compression process, as shown in FIG. 2, after the gas is compressed to overcome the biasing force of the disc spring 40, the valve 36 rises to open the discharge port 34, thereby opening the compression chamber 42.
Discharge of gas from is permitted.

The upper part of the disc spring 40 has a substantially partially cylindrical shape and faces into a groove 44 formed on the lower surface of the retainer 46, but the retainer 46 has an annular neck or columnar body 50 having a through hole in its center. is provided. The end 52 of this columnar body 50 is connected to the valve 36
is positioned such that when closed it is substantially coplanar with the lower surface of valve plate 22 and valve 36. The inner surface area of the bulb 36 defines an opening 54 that passes through the bulb 36 centrally. The dimensions of the columnar body 50 and the opening 54 located within the pressure-responsive valve 36 are set such that the columnar body 50 and the valve 36 can slide relative to each other while maintaining an airtight state via the seal ring 56. There is.

Cylinder head 6 made by casting
A hole 59 is provided in the cylinder head 60, and a re-expansion gap 58 forming a part of the hole 59 is formed in the cylinder head 60. head 60
is fastened and fixed to the compressor body 12 with the valve plate 22 in between so that the gap 58 is arranged concentrically with the body 12. Also defined in the head 60 is a discharge space 62 surrounding the cavity 58, which discharge space 62 is defined by grooves or passage holes formed in the retainer 46, as indicated schematically by reference numerals 64 and 66. or communicated with the discharge passage by a similar passage.

A plunger 68 is slidably fitted into the hole 59 in the head 60.
The hole 59 is inserted through a seal ring 74 that seals between the air gap 58 and the space above the plunger 68.
The inner circumferential surface of the holder is engaged in a sealing manner. A seal ring 152 is provided to provide a seal between the discharge space 62 and the void 58. The plunger 68 is provided with a hanging rod portion 78, and the size of the rod portion 78 is such that the plunger 68
When the rod portion 78 is in the position shown in FIG.
The opening 5 is tightly fitted into the space of the opening 54 in the opening 5.
4 is configured to block fluid movement through. In this embodiment, the rod portion 78 is configured to sealingly engage with the peripheral wall surface of the through hole of the columnar body 50 of the retainer 46 via a seal ring 80. A coil spring 82 is provided with its lower end touching the retainer 46, and the upper end of this coil spring 82 is received by the plunger 68 within a groove 84 formed in the plunger 68. The top of the plunger 68 may be slackened at a portion 76 to allow discharge pressure to be applied to the plunger 68 when the compressor is switched from a light load condition to a full load condition. Ensure sufficient pressure receiving surface and press plunger 68.
The discharge pressure acting on the top of the plunger 68 can overcome the spring 82 force and gas pressure acting on the bottom side of the plunger 68.

The plunger 68 is moved between a first position shown in FIGS. 1 and 2, in which the compressor is in a fully loaded condition, and a second position, shown in FIG. 3, in which the compressor is in a relieved condition.
An actuator is provided to quickly move the . In this embodiment, the actuator is equipped with a solenoid valve 86, and this solenoid valve 86 has a solenoid coil 8 that can be electrically actuated.
8 and a shaft 90 which can be moved to one of two positions depending on whether the solenoid coil 88 is energized or demagnetized. The shaft 90 is slidably supported in a hole 92 having an outlet 94 and an inlet 96 below it, a hollow part 98 having an open lower end, and an inlet 100 opening to the outside of the hollow part 98. It is assumed that it has been formed.

A plurality of fluid communication passages are provided to selectively guide either suction pressure or discharge pressure to the space above plunger 68. One such communication path is between the outlet 94 and the hole 5 in the head 60.
9 is provided by a passageway 102 formed in the cover plate 104. As shown in FIGS. 2 and 3, the passage 102 is connected to the cover plate 1.
Passages 106, 108 formed in 04 and head 60
The discharge space 62 can be connected to the discharge space 62 by a passage 110 formed in the discharge space 62 . Reference numerals 112 and 114 refer to suitable gaskets for providing a fluid seal between the components. A passage 11 is provided in the body of the solenoid valve 86.
6 is provided, and a passage 11 is provided in the cover plate 104.
8 are provided and these passages 116, 11
8 is the space above the plunger 68, and the head 60
It communicates with the suction space 20 via a passage 120 therein and a passage 122 in the valve plate 22.

The operation of the valve device 10 will be explained. When the solenoid coil 88 is energized, the shaft 90 is
2 to the position shown in FIG. 2, thereby cutting off the communication of the outlet 100 with the passage 116 which is connected to the suction space 20. In this way, the discharge pressure in the space inside the hole 59 above the plunger 68 is
It is conducted via passages 110, 108, 106, 102. The discharge pressure acting on the plunger 68 is equal to the pressure inside the compression chamber 42 and the plunger rod portion 78.
This exceeds the upward force caused by the spring 82 force acting on the Therefore, the plunger 68 remains in its lowered position, and the communication between the compression chamber 42 and the cavity 58 is cut off by the rod portion 78 and the seal ring 80.
This leaves the re-expansion volume of the compression chamber 42 unchanged and the compressor operates under full load conditions.

When it is desired to reduce the load on the compressor, the solenoid coil 88 is demagnetized, thereby causing the shaft 90
is lowered to the position shown in FIG. When the shaft 90 assumes the same position, the effect of the discharge pressure is cut off, and
Since the outlet 100 communicates with the passage 116, suction pressure is introduced into the space above the plunger 68. As a result, when the force of the spring 82 is combined with the gas pressure acting on the lower surface of the plunger 68, the plunger 68 can be moved upward, and the upward movement of the plunger 68 causes the gap 58 and the compression chamber to 42 are communicated with each other via the columnar body 50 of the retainer 46. The void 58 therefore increases the re-expansion volume and reduces the capacity of the compressor.

The amount of load relief can be easily adjusted by suitable inserts that limit the amount of retraction (lift) of plunger 68. Different embodiments of such inserts are shown in FIGS. 4, 5 and 6, respectively.
In the specific example shown in FIG.
30,132 are provided. These grooves 130,
A retaining ring 134 used as a stopper for restricting the upward movement of the plunger 68 is fitted into one of the retaining rings 132 . As a result, the volume of the air gap 58 is reduced and the degree of load relief is reduced compared to if the plunger 68 were allowed to rise within the hole 59 to its uppermost position. In the embodiment shown in FIG. 5, a sleeve 136 consisting of an elastic ring is inserted into the bore 59
has been inserted. The wall 138 of this sleeve 136
The height is selected to stop the plunger 68 in the desired position. It is also possible to utilize a flanged ring 140, as in the embodiment shown in FIG. In the specific example of FIG. 6, a slot 142 with an enlarged diameter is provided at the top of the head 60.
is formed to support an outwardly facing flange 144 of ring 140. Wall 14 of ring 140
6 height is selected corresponding to the amount of rise desired to be given to the plunger 68. The inserts shown in FIGS. 4-6 can be easily installed by removing the cover plate 104, inserting the insert into the hole 59, and then reinstalling the cover plate 104.

As those skilled in the art will understand from the foregoing, the present invention relates to an adjustment mechanism that has the following advantages compared to conventionally known mechanisms. That is, since the unloader is constructed as a part that is integrated with the valve device for the compressor, the size of the entire compressor device is reduced, which is advantageous in terms of installation space. In addition, the plunger 68 is connected to a solenoid mechanism 86.
The compressor moves very quickly to one of two positions under automatic control, from which pressure, temperature and other parameters are monitored to reduce the load on the compressor. In the refrigeration system used, the unloader can easily and automatically, as part of the refrigeration system, adjust the capacity to adapt to external conditions.

The pressure responsive valve 36 connects the air gap 58 and the compression chamber 42.
Since it has an opening 54 inside to provide communication between the parts, it is lightweight.
Due to this reduced weight, the valve 36 reduces the impact on the valve seat 29 when it closes. Another advantageous feature is that the column 50 acts as a guide for the valve 36 in the open position of the valve 36 in FIG. As can be seen from FIG. 2, the valve 36 slides up and down on the column 50 and is maintained in the proper position. Suction stroke of piston 16 (Fig. 1)
In turn, the post 50 also ensures that the valve 36 is properly seated against the valve seat 28.

The simplicity of the compressor load adjustment mechanism provides a high degree of reliable operation and requires no manual adjustment. A single solenoid coil 88 can be used to control both single-cylinder and multi-cylinder compressors, further reducing manufacturing costs. Note that it is of course possible to arrange separate solenoid coils and unloading mechanisms for each cylinder in a multi-cylinder compressor.

Although the embodiments described above offer the advantages described above with respect to compressor capacity regulation and valve actuation,
It has also been found that the above-described valve system improves speed, efficiency and reliability while reducing manufacturing costs in constant displacement compressors. Several embodiments of such valve devices are shown in Figures 7-13.

7-9, gas compressor 200 is generally similar to the gas compressor illustrated in FIGS. 1-6, with the exception of modifications to the discharge valve mechanism described below. Therefore, components in FIGS. 7-9 that are the same as or similar to those shown in FIGS. 1-6 are
They are designated by the same reference numerals as used in Figures 1-6.

Pressure responsive valve 23 in gas compressor 200
6 is disposed within a discharge flow opening 220 that passes through the valve plate 222 and is partially partitioned by a valve seat 228. This valve 236 has a central opening 25
4, and is slidable on the columnar body 250 between an open position in which it is spaced from the valve seat 228 and a closed position in which it is in sealing engagement with the valve seat 228.

The columnar body 250 located within the opening 254 of the valve 236 is fixed in position relative to the valve plate 222 and the head 60, and has a sleeve 258 attached and fixed thereon by force fitting or the like, Valve 236 is adapted to slide on sleeve 258. Post 250 also has an aperture 262 therethrough that allows compression chamber 42 to be opened during volume reduction as described above with respect to FIGS. 1-6.
The opening 262 communicates between the opening 262 and the gap 58 .

A substantially flat, dish-shaped elastic sealing member 256 is disposed on the outer periphery of the columnar body 250. This sealing member 256 is made of thin elastic sheet metal, for example made of spring steel, and is
Seal surface 240 on shoulder 239 of 6 and sleeve 2
and a sealing surface 260 formed on valve 236 sealingly engages both when valve 236 is in the closed position. A sealing surface 240 on the valve 236 is preferably spaced radially outwardly from the opening 254 in the valve 236 with a groove 242 therebetween. The grooved portion 242, whose depth is greatly exaggerated in FIG.
260 serves as a gap to accommodate some level differences that may exist between the two. The illustrated grooved portion 242 is formed to be inclined radially inward from the sealing surface 240 and toward the valve seat 228 when viewed in the axial direction, but the groove has a stepped and flat inner bottom surface. A mounting portion may also be provided.

The elastic seal member 256 is connected to the above-described valve 236 and the columnar body 2 when the valve 236 is in the closed position.
The valve 236 is biased by a pressure differential above and below the valve 236 into sealing engagement with the sealing surfaces 240, 260 of the valve 236. The pressure difference is created between the discharge space 62 and the compression chamber 4 during the downward stroke of the piston 16, that is, the suction stroke.
This is due to the difference in gas pressure between the two. The resilient sealing member 256 is also biased in the direction of sealing engagement described above by a disc spring 40 compressed between the flange portion 264 of the post 250 and the resilient sealing member 256. Belleville spring 40 also biases valve 236 through resilient seal member 256 into sealing engagement with valve seat 228 . The combined spring load of the disc spring 40 and the resilient sealing member 256 is such that the valve 236 will resiliently open quickly when the pressure in the compression chamber 42 reaches a predetermined value during the upward stroke of the piston 16. is preset.

In the gas compressor 200 shown in FIGS. 7-9, the flange portion 264 of the columnar body 250 is connected to the bridge-like retainer 2.
46, and the retainer 246 is supported by the valve plate 2.
22, the columnar body 250 is aligned with the valve plate 22 in the axial direction.
It is fixed to prevent it from moving away from 2. Retainer 246 and flange part 2
64 to the valve plate 222, the disc spring 40 exerts a reaction force on the valve plate 222 via the flange portion 264 and the retainer 246. Therefore, the valve 236 and the resilient seal member 256 are resiliently biased axially toward the valve seat 228.

FIG. 7 shows a load state of the compressor 200, and FIG. 8 shows a load reduction state of the compressor 200.

In another embodiment shown in FIG. 10, the gas compressor 2
02 is of substantially the same construction as the gas compressor shown in FIGS. 7-9, but has a columnar shape due to the axially depending portion 270 formed in the head 280, which is otherwise similar to the head 60 described above. A flange portion 264 of the body 250 is locked. By locking the flange portion 264 with the head hanging portion 270 in this manner, the columnar body 250 is axially aligned with the valve plate 264.
Movement in a direction away from 2 is prevented. Further, the head 280 is fixed to the valve plate 222, and the disc spring 40 is connected to the flange portion 264 and the seal member 222.
6, the disc spring 40 exerts a reaction force on the head 280, and this reaction force is applied to the head 280.
80 is connected to the valve plate 222. gas compressor 2
02 and its valve system are otherwise similar to the 7th
It is substantially the same as the gas compressor 200 and its valve device shown in FIG. No. 7-9
The structures shown in FIGS. 1 and 10 are simple and have a small number of parts, which further reduces manufacturing costs. However, the head must be precisely machined to compensate for manufacturing tolerances of the valve.

In the embodiment illustrated in FIGS. 7-10, shoulder 258
However, although a separate sleeve was provided along a portion of the columnar body 250 and secured by a press fit or the like, such a structure can be modified as shown in FIG. In the specific example shown in FIG.
Shoulder 26 for providing a sealing surface 274 on 2
8 are integrally formed. From a functional point of view, the column 272 having an integral shoulder 268 and sealing surface 274 also corresponds in function to the column 250 shown in FIGS. 7-10, and the flange portion 264 of the column 250
It has a flange portion 276 corresponding to the flange portion 276. 1st
The valve arrangement illustrated in FIG.
It is substantially identical in structure and operation to the valve arrangement shown in the figures. What should be noted is the columnar body 250
Shoulder portion 258 and columnar body 27 formed by a separate sleeve
Any of the two integral shoulders 268 may be employed in gas compressor 200 (FIGS. 7-9) and gas compressor 202 (FIG. 10), as well as other gas compressors.

FIGS. 12 and 13 each show another embodiment of the invention. With the exception that a capacity reduction mechanism is not provided, the gas compressor 204 shown in FIG.
Furthermore, the gas compressor 206 shown in FIG. 13 corresponds to the gas compressor 202, respectively. Since a capacity reduction mechanism is not provided, the columnar body 250 described above (or the columnar body 272 having an integral shoulder portion) is a dense columnar body 29.
Replaced with 0. This columnar body 290 has a flat end 292, a sealing surface 294 and a flange portion 2.
96, these include the end portion 252 of the columnar body 250, the sealing surface 260, and the flange portion 26.
4, and the end portion 273 of the columnar body 272 described above,
They correspond to the sealing surface 274 and the flange portion 276, respectively. The shoulder 298 forming the sealing surface 294 can be a separate sleeve, as described above for the column 250, or it can correspond to an integral shoulder 268, as described above for the column 272. . However, since the gas compressors 204 and 206 are not provided with a capacity reduction mechanism, the columnar body 290 is formed tightly and does not have an opening passing through it in the axial direction. The interaction between valve 236 and post 290 is substantially the same as described above with respect to Figures 7-11.

[Brief explanation of the drawing]

FIG. 1 is a longitudinal sectional view showing a part of a reciprocating gas compressor incorporating an embodiment of the valve device of the present invention having a capacity reduction mechanism, and the gas compressor is in a suction stroke under full load. . FIG. 2 is a longitudinal sectional view similar to FIG. 1, but illustrated in the compression stroke of the gas compressor. FIG. 3 is a longitudinal sectional view similar to FIG. 2, but shows a state in which the capacity of the gas compressor is reduced. FIG. 4, FIG. 5, and FIG. 6 are longitudinal sectional views each showing a specific structure of an insert used to change the volume of the gap adding gap of the capacity reduction mechanism. FIG. 7 is a longitudinal sectional view of a portion of a gas compressor incorporating another embodiment of the inventive valve arrangement with a capacity reduction mechanism, the gas compressor being at full load. FIG. 8 is a longitudinal sectional view similar to FIG. 7, but shows a state in which the capacity of the gas compressor is reduced. FIG. 9 is an enlarged longitudinal cross-sectional view of the portion indicated by the reference numeral 9 in FIG. 7. FIG. 10 is a longitudinal sectional view similar to FIG. 7, but showing another embodiment of the valve device of the present invention. FIG. 11 is an enlarged longitudinal cross-sectional view similar to FIG. 9, but showing another embodiment of the valve device of the invention in which the column has an integral shoulder. FIG. 12 is a longitudinal sectional view similar to FIG. 7, but shows an embodiment of the valve device of the present invention which does not include a capacity reduction mechanism unlike the one shown in FIGS. 1-11. FIG. 13 is a longitudinal sectional view similar to FIG. 10, but shows another embodiment of the valve device of the present invention, which does not include a capacity reduction mechanism unlike that shown in FIGS. 1-11. 10... Valve device, 14... Cylinder hole, 1
6... Piston, 20... Suction space, 22... Valve plate, 24, 26... Suction passage, 28... Valve seat, 3
4...Discharge port, 36...Pressure responsive valve, 40...
... disc spring, 42 ... compression chamber, 46 ... retainer,
50... Column body, 54... Opening, 58... Gap for adding re-expansion gap, 59... Hole, 60... Cylinder head, 62... Discharge space, 68... Plunger, 78... Rod portion, 80... Seal ring, 82
...Coil spring, 86...Solenoid valve, 88...
... Solenoid coil, 90 ... shaft, 92 ... hole,
94...Exit, 96...Entrance, 100...Entrance,
102... passage, 104... cover plate, 116,1
18, 120, 122...Aisle, 130, 132
... Groove, 134 ... Retaining ring, 136 ... Sleeve,
140...Ring, 200, 202, 204, 2
06...Gas compressor, 220...Discharge flow opening,
222... Valve plate, 228... Valve seat, 236... Pressure responsive valve, 239... Shoulder, 240... Seal surface, 246... Retainer, 250... Column body,
254...Opening, 256...Elastic sealing member, 2
58... Sleeve, 262... Opening, 260...
Seal surface, 264...flange part, 268...shoulder part, 270... hanging part, 272... columnar body, 27
4... Seal surface, 276... Flange part, 280
... Head, 290 ... Column, 294 ... Seal surface, 296 ... Flange, 298 ... Shoulder.

Claims (1)

[Scope of Claims] 1. A valve device comprising: A. a valve plate having an opening with a peripheral wall surface forming a valve seat; B. a columnar body disposed in a fixed position within the opening; C. a valve slidably disposed on the columnar body and movable between a closed position in which it engages with the valve seat and an open position in which it is spaced from the valve seat; D; a sealing member that prevents fluid flow between the valve and the columnar body when the valve is in the position, E a retainer whose position is fixed relative to the valve plate, and F between the retainer and the valve. A valve device comprising: a spring disposed in the valve for biasing the valve toward the closed position; 2. The valve device according to claim 1, wherein the seal member is made of a flexible material and is disposed between the valve and the columnar body. 3. The valve device according to claim 1, wherein the above-mentioned valve and columnar body each include:
A valve device having an annular sealing surface, the sealing member comprising an annular resilient body sealingly engaging the sealing surface when the valve is in the closed position. 4. The valve device according to claim 3, wherein the sealing surface of the columnar body is a surface integral with the columnar body. 5. The valve device according to claim 3, wherein a sleeve having the sealing surface of the columnar body is attached to the columnar body. 6. The valve device according to claim 3, wherein the seal member is made of sheet metal. 7. The valve device according to claim 3, wherein the sealing member assumes a flat plate shape when not subjected to force. 8. The valve device according to claim 3, wherein the sealing surface of the valve and the sealing surface of the columnar body are each flat and arranged on substantially the same plane. 9. The valve device according to claim 3, wherein the sealing surface of the valve is disposed on the valve on a side closer to the outer peripheral edge of the valve. 10. The valve device according to claim 9, wherein the valve is provided with a grooved portion formed by cutting out the valve material between the sealing surface and the inner peripheral edge of the valve. 11. The valve device according to claim 3, wherein the sealing member is disposed between the spring and the valve. 12. The valve device according to claim 1, wherein the valve seat has a truncated conical shape. 13. The valve device according to claim 1, wherein the valve is made of a polymeric material. 14. The valve device according to claim 1, wherein the columnar body has an opening passing through the columnar body at its center, and a rod portion is slidably disposed within the opening. A valve device provided with a plunger having a plunger. 15. The valve device according to claim 14, wherein the valve, the columnar body, and the plunger rod have their end surfaces substantially aligned on the upstream side of the valve when the valve is in the closed position. The valve device is configured such that the position of the end face is set such that the end face is located at the end face. 16. The valve device according to claim 1, wherein the columnar body has an end face substantially coplanar with an end face of the valve on the upstream side of the valve when the valve is in the closed position. Valve device formed in. 17. The valve device according to claim 1, wherein the columnar body has a portion that engages with the retainer and is prevented from moving away from the valve seat, and A valve device in which a spring is arranged so as to be compressed between the columnar body portion and the valve. 18. The valve device according to claim 17, wherein the sealing member is disposed between the spring and the valve. 19. The valve device according to claim 1, comprising a bridge member attached to the valve plate so as to straddle the opening of the valve plate,
A valve device in which the columnar body is supported by the bridge member. 20. The valve device according to claim 1, which is disposed in a gas compressor between a cylinder head and a cylinder block, facing the compression chamber. 21. The valve device according to claim 20, wherein the columnar body is supported by the cylinder head. 22. The valve device according to claim 20, wherein the cylinder head has a hole for providing a re-expansion gap addition space, and the columnar body has the columnar body in its center. A valve device comprising plungers each having an aperture therethrough, the plunger being slidably fitted in the aperture and having a stem movable into and out of the aperture. 23. The valve device according to claim 22, which is an actuator for selectively moving the plunger, the actuator moving the rod portion of the plunger into the opening of the columnar body. a first position in which the compressor is completely loaded by cutting off communication between the compression chamber and the gap; A valve assembly including an actuator selectively positioned in communication with a second position to relieve a load on a compressor. 24. The valve device according to claim 23, wherein the plunger has an arm portion having a substantially T-shaped cross section and occupying the entire width of the hole. 25. The valve device according to claim 23, wherein the actuator is a suction pressure source,
A discharge pressure source with a pressure greater than the suction pressure, and the plunger is placed within the hole to selectively communicate with either the suction pressure source or the discharge pressure source on the opposite side from the gap. A valve device equipped with a solenoid valve. 26. The valve device according to claim 25, wherein the plunger is provided with a recessed portion formed by cutting out the plunger on the opposite side of the rod portion. 27. The valve device according to claim 25, wherein the valve device is connected to the plunger and is energized to move the plunger in a direction in which the rod portion thereof is moved to the second position. a spring means configured to have a relatively small spring load so as to enable the rod of the plunger to be moved to the first position when the discharge pressure is applied to the plunger; A valve device provided with spring means. 28. The valve device according to claim 27, wherein the spring means is connected at one end to the arm portion of the plunger and at the other end to the retainer. 29. The valve device according to claim 23, wherein the actuator is a solenoid valve device disposed on the cylinder head and moves in response to excitation magnetization of a solenoid coil and the solenoid coil. a solenoid valve device having a shaft therein, the shaft disposed within the hole, the plunger being disposed within the hole, and selectively controlling suction pressure or discharge pressure of the compressor on the side opposite to the cavity; It is a passage for guiding the solenoid coil to the suction pressure in one state, and the discharge pressure in the other state.
A valve device having passages arranged and formed to respectively lead thereto. 30. The valve device according to claim 29, wherein the actuator has a first passage for guiding suction pressure to the passage in the shaft;
A second passage for guiding discharge pressure to the passage in the shaft, and communicating the passage in the shaft with the inside of the hole located on the opposite side of the gap with the plunger apart. A third passageway. 31. The valve device according to claim 23, wherein the stopper means is inserted into the hole of the cylinder head and moves the plunger in a direction to communicate the compression chamber and the gap. A valve device comprising a stopper means that comes into contact with the plunger to control the volume of the gap and adjust the degree of load reduction of the compressor when the plunger is in contact with the plunger. 32. The valve device according to claim 31, wherein the stopper means is fitted and held in at least one groove formed in the inner circumferential wall of the hole of the cylinder head. and a retaining ring having an inner diameter smaller than an outer diameter of the plunger. 33. The valve device according to claim 31, wherein the stopper means is a ring inserted into the hole of the cylinder head and has a length corresponding to the degree of load reduction to be applied to the compressor. A valve device comprising a ring having dimensions. 34. The valve device according to claim 33, wherein a slotted hole having an inner diameter larger than that of the hole is formed in the end surface of the cylinder head on the opposite side from the compression chamber, The valve device wherein the ring includes a flange fitted into the slot.