JPS60249775A - Valve gear - Google Patents

Abstract

(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

DETAILED DESCRIPTION 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.

A typical reciprocating piston type gas compressor has a pressure-responsive suction and discharge valve mechanism fully assembled between the head portion and the compression chamber at the cylinder end. An area of a gas compressor that is large enough to allow the maximum volume of gas flow under an acceptably small pressure drop during a given period of time during the entire production period of the gas compressor. It is important to give the full amount. This thing! This is important since air conditioning systems generally require a relatively large flow rate in refrigeration compressors used in air conditioning systems. In addition to the desire to maximize boat area for a cylinder of a given size, it is also important to reduce the weight of the movable valve member and limit the inertial effects of the valve member, as well as the noise generated by the valve gear, especially in high speed compressors. In such gas compressors it is also important to minimize the re-expansion volume, crevice volume at the pulp side end of the cylinder. Therefore, the compression chamber end wall should have a shape that is complementary to the top of the piston so that the piston can minimize the total volume of the compression chamber without restricting gas flow during its webbing stroke. be. This request can be met by creating a composite piston head shape, but composite pistons are extremely expensive to manufacture and difficult to assemble. Throttling losses often occur as the piston approaches top dead center. 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 installations), it is required to fully control or reduce the capacity of the gas compressor. The need for adjustment of compressor capacity requires that the refrigeration system be made to operate with variable heating and cooling power to fully balance the heat inflow load at the selected temperature for the evaporator. This occurs when a fixed displacement pump is used in the system. The compressor capacity load 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. As 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 total refrigerant flow rate. Therefore, if the refrigeration system is not equipped with a capacity control means, the suction pressure will decrease due to a decrease in the refrigerant flow rate. Therefore, the capacity of the compressor is reduced when the compressor operates with a relatively high compression ratio and a relatively low volumetric efficiency. Such capacity reductions can be tolerated to a certain extent and are typically not taken into account in the design of refrigeration systems. However, the minimum suction pressure or suction temperature at which the compressor or the entire refrigeration system should not be operated, such as the saturation suction temperature at which frost begins to form on the coil of an air-cooled evaporator, and 2) the minimum limit of the water cooler. temperature, is O In some cases, especially in low temperature refrigeration systems, to overcome these problems in relatively small refrigeration systems, if the compression ratio becomes excessive due to the reduction in flow rate, the compressor will overheat. Simple means such as using a thermostat or a suction pressure responsive switch to start and stop the compressor can all be used. 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.
These include high-temperature gas branch flow type unloaders,
There are suction gas cutoff type unloaders, unloaders with a mechanism to fully raise the suction valve, and unloaders with a full re-expansion gap and additional air gap.In the type of unloader with a re-expansion gap and additional air gap, the cylinder is separated from the Eri cylinder by a stomb valve, etc. This void is utilized to reduce the volumetric efficiency of the additional re-expansion volume or re-expansion gap adding compressor.

The conventional capacity reduction mechanism that makes full use of the gap added has 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.

Previous types of devices provide additional interstitial volume;
It is said that the pulp or piston is adjusted artificially. Although another prior art technique has been utilized to control a relatively small number of low speed compressors, manual adjustment is impractical in today's air conditioning or refrigeration systems where automatic control is desired. In addition, the previous device was installed on January 1, 1983.
A pulp device for a compressor developed by the applicant, as disclosed in U.S. Pat. Excellent sealing has been achieved, making it noiseless and quiet operation, making it well suited for high speed compressors, making it impossible to integrate into pulp equipment.

Problems of the Invention This invention first relates to a gas compressor, whether or not 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 described in Part 1 of the prior art and its problems and is suitable for use as a discharge valve. That is, the purpose of this invention is to increase the efficiency of a gas compressor or similar fluid transport machine, improve the discharge flow characteristics when pulp rises, and prevent permanent deformation of the pulp member. It improves the sealing properties of pulp without any waste, allows compressors to operate quietly and smoothly, and can be suitably used in high-speed compressors.

We are providing a new pulp storage facility.

Another object of the present invention is to provide the prior art and its second problem.
In connection with the above-mentioned points, it is an object of the present invention to provide a novel pulp apparatus, which is a valve apparatus as described above, which can include an unloader of the type provided with a re-expansion gap. Structure and effect of the entire pulp apparatus according to the present invention, including the unloader,
If the gas compressor is provided with a mechanism that allows its capacity to be reduced, an opening is formed in the pulp for the gas compressor through which it is re-expanded. A hole for adding the entire gap is formed. The plunger, which is slidably fitted into the hole, is provided with a rod that extends into the hollow cylindrical column disposed within the opening of the pulp. The plunger described above is capable of moving the compressor to a first position in which communication between the compression chamber of the compressor and the air gap is interrupted and the compressor is placed in a fully loaded condition. Further, the plunger is adapted to be pulled out from the above-mentioned opening of the pulp to communicate between the above-mentioned compression chamber and the void and to be able to pressurize the pulp.

When the pulp apparatus according to the present invention is embodied as one for a gas compressor equipped with a capacity reducing device, the above-described structure allows the discharge valve mechanism to form a part of the capacity reducing mechanism for expanding the gap volume. A compact device can be obtained. The weight of the discharge valve is reduced, which reduces the impact on the valve seat when the pulp closes.

In a preferred embodiment, a retainer is provided having a hollow column portion that serves to guide the pulp during its movement and seating on the valve seat. 1cld between the pulp and the columnar body part, in order to enable the pulp to be disposed on the columnar body part in a sealed and slidable manner, and to provide a buffering effect to reduce the impact of the pulp. In another embodiment of the invention, a solenoid is used to rapidly move the plunger compressor capacity to a non-relief position or a relieved position. Capacity control therefore automatically determines the amount of retraction of the plunger into the hole in the head with an insert or sleeve that can change the manual adjustment method and the clearance volume added by the air gap. can be inserted alternately to correspond to the desired degree of capacity reduction.

The present invention provides a pulping apparatus that is inexpensive, simple, operates with high efficiency in gas compressors and other fluid transport machinery, and has all the advantages of the pulping apparatus disclosed in the aforementioned U.S. Pat. This is what we provide. In other words, the present invention reduces the friction between the above-mentioned two columnar bodies and the pulp in fluid transport machines such as gas compressors, and operates smoothly at high speed. To provide a pulp equipment with excellent seal properties between the body and the pulp.

According to the present invention, an opening is formed through the pulp movable between a closed position and an open position, one position is fixed, a columnar body is fitted and supported in the opening, and the columnar body allows the pulp to be moved between the closed position and the open position. is slidably guided between an open position and a closed position.

This is provided by providing a sealing member that prevents fluid flow to and from the body.

In one embodiment of the present invention, the above-mentioned sealing member is provided as follows: The pulp is provided with a shoulder portion having a sealing surface at a distance from the opening in an outward direction; The column is also provided with a shoulder having a sealing surface. The elastic sealing member is disposed so as to sealingly engage with both the sealing surface of the pulp and the sealing portion of the columnar body when the pulp is in the closed position. Prevent fluid leakage between the Such a seal member can be elastically deflected while the pulp slides between the open position and the closed position, and does not come into sliding contact with the columnar body. The sealing member is biased by the pressure difference between the gas pressures acting on both sides of the pulp in a direction into sealing engagement with the two sealing surfaces described above when the pulp is in the closed position; Furthermore, it is desirable to provide a spring that biases the seal member in the above-mentioned direction so as to be compressed between the seal member and the valve device fixing portion.

In a preferred embodiment of the present invention, the above-mentioned pulping apparatus comprises:
Used as a discharge valve device for reciprocating piston type gas compressors. In this embodiment, the valve plate Vt has a valve sheet metal biasing having a through opening defining a valve seat, the pulp sealingly engaging said valve seat in its closed position. Preferably, the pulp and the column have a flat end surface at the end opposite the shoulder, and the end surface of the pulp and column and the inner end surface of the valve plate are mutually aligned when the pulp is in the closed position. In this way, the two ends and the inner end surface, which are located on the same plane at the pulp closing position, are at the end of the compression chamber of the compressor, and the re-expansion volume in the compression chamber is expanded. Since the capacity of the compressor is not reduced and the volume is minimized, it is advantageous when the capacity of the compressor is not reduced and when a mechanism for performing the same reduction is not provided. An example in which an embodiment of the apparatus is used in a gas compressor will be illustrated.As will be understood from the following description, the pulp apparatus according to the present invention can be used in other fluid transport machines other than the illustrated compressor or heat pump. is also available.

1-3, a pulp unit with an unloader mechanism, designated generally by the reference numeral 10, is shown at f along with a reciprocating gas compressor. The compressor body 12, which is a cylinder block, includes a reciprocating piston 16 having a seal ring 18.
It is equipped with a 14K cylinder hole to accept the
A suction space 20 adjacent to this cylinder hole 14 is formed.
ing.

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.

The valve plate 22 has a plurality of suction passages 24,26ffi communicating with the suction holes 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 normal reed valve type suction valve has a portion 3 which performs a pulping action and is located opposite the suction passages 24 and 26 which are connected to each other.
0.32'.

The discharge port 34 passes through the valve plate 22f and is partitioned by the valve seat 28. A pressure-responsive pulp 36 is disposed within the discharge port 34, and the lower end portion of the pulp 36 has a truncated conical shape and can be held in a sealing manner against the valve seat 28. If the pressure-responsive pulp 36 is urged by the suction pressure during the suction stroke of the piston 16 and engages the valve seat 28 in a sealing manner, the pressure-responsive pulp 36 is acted upon through the protective shim 40. The disc spring 40 is biased to move in the direction of engagement with the valve seat 28. During the compression process, as shown in FIG. 2, after the pulp 36 has compressed the gas until it overcomes the biasing force of the disc spring 40, it rises to open the discharge port 34, thereby removing the gas from the compression chamber 42. Gas discharge is allowed.

The upper part of the disc spring 40 has a substantially partially cylindrical shape: the retainer 46 has a groove f17 formed on the lower surface facing into the concave groove 44, and the retainer 46 has an annular neck or a through hole in the center. Columnar bodies 5o are provided. The end 52 of this column 5o is positioned so that it is substantially flush with the lower surface of the valve plate 22 and the pulp 36 when the pulp 36 is closed. By the inner surface area of the pulp 36,
An opening 54 passing through the pulp 36 at the center is defined. Column bodies 50 located within the pressure-responsive pulp 36
The dimensions of the opening 54 and the columnar body 50 are set so that the columnar body 50 and the pulp 36 can slide relative to each other while maintaining an airtight state via the seal ring 56.

Siligas made by casting molding, F
A hole 59 is provided in the hole 59.
The air gap 58 for adding re-expansion gap, which forms part of the cylinder
It is formed within the head 60. Hecht 60 is valve plate 22
Tightening is fixed with respect to the compressor body 12 in such a way that the gap 58 is arranged concentrically with the body 12. Head 60 inside.

A discharge space 62 surrounding the cavity 58 is formed, which discharge space 62 is formed by a groove 1, passage hole or similar passage formed in the retainer 46, as indicated schematically by reference numerals 64 and 66. It communicates with the machine discharge passage.

A plunger 68 is slidably fitted into the hole 59 in the head 60, and the plunger 68 is connected to the hole 59V via a seal ring 74 that seals between the cavity 58 and the space above the plunger 68. It is engaged in a sealing manner with respect to the inner circumferential surface. 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 bellows-shaped rod portion 781 whose dimensions are such that when the plunger 68 is in the position shown in FIGS. The opening 54 is configured to tightly fit into the space of the opening 54 to block fluid movement through the opening 54. 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 500 of the retainer 46 via a seal ring 80. A coil spring 82 whose lower end is in contact with the retainer 46 is provided, and the upper end of this coil spring 82 is connected to the recess 1 formed in the plunger 68.
! 84 and is received by the plunger 68.

The top of the plunger 68 may be slackened at a portion 76 so that the full discharge pressure is applied to the bluffer 68 when the compressor is switched from a light load condition to a full load condition. By ensuring a sufficient pressure receiving surface, the discharge pressure acting on the top of the plunger 68 can overcome the force of the spring 82 and gas pressure acting on the lower surface of the plunger 68ρ.

1.2 with the compressor at full load.
An actuator is provided to rapidly move the plunger 6B between the position shown in FIG. In this embodiment, the actuator is equipped with a solenoid valve 86.
% This solenoid valve 86 has an electrically actuable solenoid coil 88 and an axis that moves it to one of two positions depending on whether the solenoid coil 88 is energized or de-energized. 90. axis 90
is slidably supported in the outlet 94, the inlet 96 below it, and the hole 92 with the metal plate, and has a hollow part 98 whose lower end is completely open and an inlet 10oIl which opens into the hollow part 98 and the outside side. :
It is said that it is formed in

A plurality of fluid communication passages are provided for selectively guiding suction pressure or discharge pressure to the space above the plunger 68. 〃・One of the connecting passages is
A passageway 102 is provided in cover plate 104 to connect outlet 94 to the top of hole 59 in head 6o. As shown in FIG. 2-3, the passage 102 is
Passages 106, 108 formed in cover plate 104 and head 6
A passage 110 formed in the o and K can be connected to the discharge space 62. Reference numerals 112 and 114 refer to appropriate gaskets to provide a complete fluid seal between the components.In the body of the solenoid valve 86 there is a passage 116 and in the cover plate 104 a passage 118 is provided. These passages 116. ] 18 is a space above the plunger 68 and a passage 120 in the head 6o and a passage Nr 12 in the valve plate 22.
2? It is designed to be in communication with the suction space 20 through the air.

The entire operation of the pulping device 10 will be explained. Solenoid coil 8
8 is energized, the shaft 90 is raised to the position shown in FIGS. . Thus, a discharge pressure is generated in the space inside the hole 59 above the plunger 68.

Passages 110, 108, 106, 102 are conducted through the gold. The discharge pressure acting on the plunger 68 exceeds the upward force due to the pressure within the compression chamber 42 and the force of the spring 82 acting on the planar rod portion 78. Therefore, plunger 68 remains in its lowered position 2', and communication between compression chamber 42 and cavity 58 is cut off by rod portion 78 and seal ring 80.

The re-expansion volume of the compression chamber 42 remains unchanged and the compressor operates under full load.

When you want to reduce the load on the compressor, use a solenoid coil8.
8 is demagnetized, cnyc, so axis 90' is the third
Lower to the position shown in the figure. When the shaft 9o assumes the same position, the suction pressure is not introduced into the space above the plunger 68 since the Vck outlet 100 communicates with the passage 1.16 when the discharge pressure is cut off.

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 6
By moving the plunger 68 upward, the air gap 58 and the compression chamber 42 are brought into communication via the columnar body 50 of the retainer 46. Therefore, the void 58 increases the re-expansion volume n1
Compressor capacity is reduced.

The amount of load reduction can be easily adjusted by the amount of retraction of the plunger 68 (by means of a suitable insert VC which limits the rise. η). Different examples of such inserts are given in Section 4.5.6.
Each is shown in the figure.

In the specific example shown in FIG. 4, the hole 590 is
a plurality of grooves 130, 132 spaced apart from each other in the axial direction of the
Fully equipped. These grooves 13o.

One of the 132 is the rising IC of the plunger 68! A wheel 134 used as a stone bar for full restriction is fitted.
Ru. As a result, the volume of the cavity 58 is increased, and the amount of load reduction is reduced compared to the case where the plunger 68 is configured to be able to rise to the uppermost position within the hole 59. Fifth
In the embodiment shown in the figures, a sleeve 136 consisting of an elastic ring f is inserted into the hole 59. The wall 138 height of this sleeve 136 is selected to stop the plunger 68t at the desired position. It is also possible to utilize a flanged ring 140, as in the embodiment shown in FIG. In the embodiment of FIG. 6, an enlarged diameter slot 142 is formed in the top of the head 60 to receive an outwardly facing flange 144 of the ring 140. The height of the wall 146 of the ring 140 is selected to correspond to the amount of lift desired to be imparted to the plunger 68. The inserts shown in Figures 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 104fc.

Having said the above, a person skilled in the art can understand from Yoneko and Oro,
The present invention relates to an adjustment mechanism that has the following advantages compared to conventionally known mechanisms. That is, since the adder 70 is constructed with a part that is integral with the pulp apparatus for the compressor, the size of the entire compressor apparatus is reduced and installation is advantageous in terms of space. The plunger 68 also moves very quickly to one of two positions under automatic control by a V-noid mechanism 86, which monitors pressure, temperature, and other parameters of the compressor. load? In a refrigeration system that is used as a condition for mitigation, the unloader can easily, as part of the refrigeration system, automatically and quickly adjust its capacity to adapt to external conditions.

The pressure-responsive pulp 36 reduces the impact on the valve seat 29 when it closes due to the reduced weight of the air gap 58 and the compression chamber 42. Another advantageous feature is that the columnar bodies 5o act as guides for guiding the pulp 36 in the state shown in FIG. be. As can be understood from FIG.
Ru. During the suction stroke of the piston 16 (FIG. 1), the columnar body 50
also ensures that the pulp 36 is properly seated against the valve seat 28.

The simplicity of the compressor load adjustment mechanism provides a high degree of reliable operation - no manual adjustment is required. A single flenoid coil 88 can be used to control all single-cylinder and multi-cylinder compressors, thereby further reducing manufacturing costs. In a multi-cylinder compressor, it is of course possible to provide each cylinder with a separate solenoid coil and unloading mechanism.

Although the embodiments described above offer all the advantages mentioned above with respect to volume regulation and valve actuation of the pressure mYIA, the pulp apparatus described above also reduces manufacturing costs in fixed displacement type compressors.
Improving speed, efficiency and reliability while saving money,
Several embodiments of pulping equipment with the heading to 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. For this reason, the seventh
- In Figure 9, components that are the same as or similar to those shown in Figures 1-6 are designated by the same reference numerals as used in Figures 1-6. A responsive pulp 236 is disposed within a discharge flow opening 220 that extends through the valve plate 222 and is partially partitioned by a valve seat 228. The pulp 23G has a central aperture 254 and is slidable over the column 250 between an open position away from the valve seat 228 and a closed position sealingly engaged against the valve seat 228.

The columnar body 250 in the opening 254 of the pulp 236 is in a position relative to the valve plate 222 and the opening 254.
It has a fixed sleeve 9 and a sleeve 258 fixed thereon by press fitting or the like.

The pulp 236 is rubbed on the sleeve 258! I'm so angry. The column 250 also has a portal 262 extending therethrough, as described above with respect to FIGS. 1-6. r. During the reduction, the space between the compression chamber 42 and the air gap 58 is made to pass through the opening 262vc.

An elastic sealing member 256 having a flat and dish-like shape is attached to the columnar body 2.
It is arranged at the outer peripheral position of 5Q. This seal member 25
6 is made of a thin elastic sheet metal made of spring steel, for example, and includes a sealing surface 240 on the shoulder 239 of the pulp 236 and a sealing surface 260 formed on the sleeve 258.
and are sealingly engaged when the pulp 236 is in the closed position. A sealing surface 240 on the pulp 236 is preferably spaced radially outwardly from the opening 254 in the valve 236 with a grooved portion 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.
However, a grooved section having a stepped and flat inner bottom surface can also be provided.

The resilient sealing member 256 is energized by a pressure difference above and below the pulp 236 so as to sealingly engage the pulp 236 and the sealing surfaces 240, 260 of the columnar body 250 when the pulp 236 is in the closed position. . This pressure difference is generated in the discharge space 6 during the downward stroke of the piston 16 and the suction stroke of the piston 16.
This is due to the difference in gas pressure between the compression chamber 2 and the compression chamber 42.

The resilient sealing member 256 is then directed in the above-mentioned direction of sealing engagement.
7272 portion 264 of columnar body 250 and elastic seal member 25
It is also energized by a disk spring 40 which is compressed between 6 and 6. The disc spring 40 also connects the pulp 23 via an elastic seal member 256.
61. The pulp 236 is energized to engage a sealing force against the valve seat 228. Belleville spring 40 and elastic seal member 25
When the pressure in the compression chamber 42 reaches a predetermined value during the upward stroke of the screw 716, the pulp 2
36 is preset to a value that causes it to open elastically and quickly.

In the gas compressor 200 shown in FIGS. 7-9, the columnar body 250
The flange portion 264 of is supported by the bridge-like retainer 246.
The retainer 246 is attached to the columnar body 2 with respect to the valve plate 222.
50 is fixed to prevent any movement away from the valve plate 222 in the axial direction. Since the retainer 246 and the flange portion 264t are both connected 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. Accordingly, the pulp 236 and the resilient sealing member 256 are resiliently biased toward the valve seat 228 in the axial direction.

Figure 7 shows the load condition of the compressor 200, and Figure 8 shows the load condition of the compressor 2.
00 load reduction states, respectively.

In another embodiment illustrated in FIG. 10, the gas compressor 202 is
The 7th to 9th reasons are that the columnar body 250 has a structure similar to that of the illustrated gas compressor, but is formed in the head 280, which is similar in other respects to the head 60 described above, by a hanging portion 270 in the axial direction. The flange portion 264i is locked. By locking the 1 ref flange portion 264 to the head hanging portion 270 in this manner, the columnar body 250 is aligned with the valve plate 22 in the axial direction.
Movement in the direction away from 2 is prevented.

Further, since the head 280 is fixed to the valve plate 222 and the disc spring 40 is compressed between the flange 5264 and the seal member 256, the disc spring 40 exerts a reaction force on the head 280, and this reaction force is transmitted to the valve plate 222 because the head 280 is connected to the valve plate 222. Gas compressor 202 and its pulping apparatus are otherwise substantially similar to gas compressor 200 and its pulping apparatus illustrated in FIGS. 7-9. $7-9
The structure shown in FIGS. 1 and 10 is simple with a small number of parts, and further reduces manufacturing costs.

However, on the other hand, the head needs to be precisely machined to compensate for all pulp manufacturing tolerances.

In the embodiment illustrated in FIGS. 7-10, the shoulder 258 included a separate sleeve secured by a press fit or the like along a portion of the column 250; can be changed to . In the embodiment shown in FIG. 11, a companion shoulder 268 is integrally formed on the columnar body 272 to provide a sealing surface 274. Functionally
A column 272 having an integral shoulder 268 and a sealing surface 274 also corresponds in function to column 250 shown in FIGS. 7-10 and has a flange portion 276 corresponding to column 2500 flange portion 264. There is. The pulping apparatus illustrated in FIG. 11 is otherwise the pulping apparatus illustrated in FIGS. 7-10;
They are substantially the same both in structure and function. It should be noted that either the separate sleeve shoulder 258 of column 250 or the integral shoulder 268 of column 272 can be used for gas compressor 200 (Figures 7-9) and gas compressor 202 (Figure 10).
(Fig.) and 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 illustrated in FIG.
to the gas compressor 200.

Furthermore, the gas compressor 206 shown in FIG. Column body 272) with integral shoulders
is replaced with a dense columnar body 290. This columnar body 290 has a flat end portion 292, a sealing surface 294, and a flange portion 296, which are similar to the end portion 252, sealing surface 260, and flange portion 264° of the columnar body 250 described above, and the columnar body 272 described above. End portion 273, sealing surface 27
4 and the flange portion 276, respectively. The shoulder portion 298 that completely forms the sealing surface 294 is the columnar body 25
It could be a separate sleeve, as described above for column 272, or it could correspond to an integral shoulder 268, as described above for column 272. However, the capacity of the gas compressors 204 and 206 is reduced: since no shallow grooves are provided, the columnar body 290 is formed to be dense, and the columnar body 290 has no openings passing through it in the axial direction. The interaction with the columnar body 290 is the seventh
-11 is substantially the same as described above with respect to FIG.

[Brief explanation of the drawing]

FIG. 1 is a longitudinal sectional view showing a part of a reciprocating gas compressor in which an embodiment of the present invention's gas compressor is fully incorporated, which is equipped with a capacity reduction mechanism. Fig. 2 is a longitudinal sectional view similar to Fig. 1, but the compression stroke of the gas compressor is illustrated. Fig. 3 is a longitudinal sectional view similar to Fig. 2, but the gas Figures 4 and 5 show the state in which the capacity of the compressor is fully reduced.
6 and 6 are longitudinal cross-sectional views showing a specific structure of an insert used to completely change the volume of the gap adding gap of the n1 capacity reduction mechanism. FIG. 7 is a vertical cross-sectional view of a gas compressor incorporating another embodiment of the present invention) having a capacity reduction mechanism, and showing the gas compressor at full load. FIG. 8 is a longitudinal sectional view similar to FIG. 7, but shows the gas compressor in a state where the capacity is reduced by 11. Figure @9 is an enlarged vertical cross-sectional view of the portion indicated by the reference numeral 9 in Figure 7. FIG. 10 is a longitudinal sectional view similar to FIG. 7, but showing another embodiment of the pulping apparatus of the present invention. FIG. 11 is an enlarged longitudinal section similar to FIG. 9; it is made of oak, but shows another embodiment of the pulping apparatus of the invention in which the columns have integral shoulders. FIG. 12 is a longitudinal sectional view similar to FIG. 7. 1-11 shows an embodiment of the pulp apparatus of the present invention which does not include a capacity reduction mechanism different from that shown in FIGS. 1-11. FIG. 13 is a longitudinal sectional view similar to FIG. 10. 1-11 shows another embodiment of the pulp apparatus of the present invention which does not include a capacity reduction mechanism unlike the one shown in FIGS. 1-11. IO...Pulp device, 14...Cylinder hole, 16.
... Piston y120... Suction space, 22... Valve plate,
24゜26... Inhaler! 3% 28...-valve seat%3
4...Discharge port %36...Pressure responsive pulp, 40...
・Disc spring, 42...compression chamber. 4"6...retainer, 50...column, 54...
Opening, 58... Gap for adding re-expansion gap, 59...
Hole, 60... Cylinder head, 62... Discharge space,
68... Plunger, 78... Rod portion %80... Ring ring, 82... Coil spring, 86...
Solenoid valve, 88... solenoid coil, 90... shaft,
92...hole, 94...exit, 96...inlet, 10
0... Entrance, 102... Passage i, 104... Cover plate, 116, 118, 120.122... Passage. 130.132...Groove, 134...Retaining ring, 136.
... Sleeve, 140 ... Ring, 200, 202,
204. . 206... Gas compressor, 220... Discharge flow opening,
222...Valve plate, 228...Valve seat %236...Pressure responsive pulp. 239... Shoulder part, 240... Seal surface, 246...
Retainer, 250... Column body, 254... Opening, 2
56... Elastic sealing member, 258... Sleeve, 2
62... Opening, 260... Seal surface, 264...
flange part. 268... Shoulder part, 270... Drooping part, 272...
Column, 274... Sealing surface % 276... Flange, 28°... Head, 290... Column, 29
4...Seal surface, 296...Flange part, 298...
・Shoulder area. Figure 7 Figure 2 Figure 7 ρ

Claims (1)

[Claims] 1. A pulping device comprising: A. a valve plate having an opening with a peripheral wall surface that completely forms a valve seat; B. a column f'L'fc disposed in a fixed position within said opening; and 5 C6 a closed position slidably disposed on said column and engaged with said valve seat; a pulp movable between an open position spaced from the seat; D. a seal member for preventing fluid flow between the pulp and the column when the pulp is in the closed position; , a retainer that is completely fixed in position relative to the valve plate; F. a spring that is disposed between the retainer and the pulp and biases the pulp to move in the closing direction; pulp equipment. 2. The pulp apparatus according to claim 1, wherein the sealing member is made of a flexible material and is disposed between the pulp and the columnar body. 3. The pulp device according to claim 1, wherein the pulp and the columnar bodies each have an annular sealing surface, and the sealing member is configured so that the pulp is in the closed position. A pulping apparatus comprising an annular elastic body that sealingly engages the sealing surface at one time. 4. The pulp apparatus according to claim 3, wherein the sealing surface of the columnar body is integral with the columnar body. 5. The pulp apparatus according to claim 3, wherein a sleeve provided with the sealing surface of the columnar body is attached to the columnar body. 6. Liability The pulp apparatus according to claim 3, wherein the sealing member is made of sheet metal. γ The pulp apparatus according to claim 3, wherein the sealing member has a flat plate shape when not subjected to force. 8. The pulp apparatus according to claim 3, wherein the sealing portion of the valve and the sealing surface of the columnar body are
A pulping apparatus, each of which is flat and arranged substantially coplanar. 9. The pulp apparatus according to claim 3, wherein the sealing portion of the valve described above is arranged on the pulp on the side near the outer periphery of the valve. io, IVjClaim m9 The pulp apparatus according to claim 9, wherein the above-mentioned valve is provided with a grooved part formed by cutting out the bump material between the seal face and the inner peripheral edge of the valve. . 11.% The pulp device according to claim 3, wherein the sealing member is disposed between the spring and the group. 12. A pulp apparatus according to claim 1, wherein the valve seat has a truncated conical shape. 13.% Permissible The pulp device according to claim 1, wherein the valve is made of a polymeric material. 14. The pulping apparatus according to claim 1, wherein the columnar body has an opening passing through the columnar body in the center thereof, and a rod portion is slidably disposed within the opening. Pulp equipment equipped with 7-jar metal for scraping gold. 15.% Permissible The pulp apparatus according to claim 14, wherein the valve, the columnar body, and the plunger rod have their end faces on the upstream side of the valve when the valve is in the closed position. A valve mounting device in which the positions of the end faces are all set so that they are approximately aligned. 16.% Allowance The pulping apparatus according to claim M1, wherein the columnar body has an end surface substantially coplanar with an end surface of the valve on the upstream side of the valve when the valve is in the closed □ position. Pulp equipment that is configured to hold. 17. The pulp apparatus according to claim #1, wherein the columnar body engages with the retainer and the valve seat η
・The spring has a portion that prevents movement in a direction away from the spring. , a pulp apparatus arranged to undergo compression between the above-mentioned columnar part and the valve. 18. The pulp apparatus according to claim 17, wherein the sealing member is disposed between the spring and the valve. 19.% Permissible Scope of Claims 1. The pulp apparatus according to claim 1, further comprising a bridge-like member attached to the valve plate so as to straddle the opening vi of the valve plate, and the columnar body is A pulp apparatus that is fully supported by the bridge-like member. 2. A pulp apparatus comprising one valve cabinet according to claim 1, which is disposed in a gas compressor between a cylinder head and a cylinder block so as to face a compression chamber. 2. A pulp apparatus according to claim J20, in which the columnar body is supported by the cylinder head. 2. The pulp apparatus according to claim 20, wherein the cylinder head has a hole for providing a re-expansion gap addition space, and the columnar body has a hole in the center thereof. a plunger having an opening passing through each of the holes, the plunger being slidably fitted in the hole and movable into and out of the opening; 23. The pulp apparatus according to claim 22, wherein the plunger 1Fr is an actuator for selectively moving the rod portion of the plunger.
The compressor is moved into the opening of the columnar body to cut off the communication between the first compression chamber and the space, and the compressor is fully loaded t'Lf.
a first position where the VC is in the c state, a second position where the VC is pulled out from the opening of the columnar body to communicate the compression chamber and the void space, and reduce the load on the compressor; Pulp equipment that is equipped with an actuator to make it. 2. 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. 2. The valve device according to claim 23, wherein the actuator includes a suction pressure source, a discharge pressure source with a pressure greater than the suction pressure, and the plastic in the hole.
The valve device is completely equipped with an electromagnetic valve for selectively communicating one of the above-mentioned suction pressure source and discharge pressure source on the side opposite to the gap across the jar. 2. The valve device according to claim 25, wherein the plunger vC% is provided with a hollow portion cut out on the opposite side of the 4ff recording rod portion. 26. The valve device according to item 25, wherein a spring is connected to the plunger and urges the plunger to move in a direction in which the rod is moved to the second position. means, wherein the spring load is set relatively low to enable the rod of the plunger to be moved to the first position when the discharge pressure is not applied to the plunger. A certain spring means is provided in the valve device 02&
28. A valve device according to claim 27, wherein the spring means is connected at one end to the arm portion of the aforementioned plunger and at the other end to the retainer.
A valve device with a connection. 2. The valve device according to claim @23, wherein the actuator is a solenoid valve device t' disposed on the cylinder head, and the actuator is a solenoid valve device t' disposed on the cylinder head, and the solenoid coil is excited and magnetized by the solenoid coil. A solenoid valve device having a shaft that moves in response to the bias, the shaft inside which the plunger discharges the full pressure in the hole and the suction pressure of the compressor on the side opposite to the air gap. This is a passage for selectively guiding the discharge pressure, and when the solenoid coil is in the negative state, the suction pressure is supplied, and in other states, the discharge pressure is supplied. A valve device having passages arranged and formed to 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, and a discharge pressure to the passage in the second shaft. A second passageway for introducing pressure, and a third passageway that communicates the passageway in the shaft with the inside of the hole located on the opposite side of the gap from the plunger. valve device. 31. The valve device according to claim 23, wherein the plunger is inserted into the hole of the cylinder head and is a means for a stopper, and the plunger communicates the specific compression chamber with the air gap. A valve device (032, claimed in the patent claim) comprising a stopper means for controlling the volume of the gap and adjusting the degree of load reduction of the compressor by coming into contact with the plunger when the plunger is moved in the direction. 32. The valve device according to item 31, wherein the stopper means is fitted and held in at least one groove formed in the inner circumferential wall of the hole in the cylinder head, and the plunger and an upper ring having an inner diameter smaller than an outer diameter of the valve. 33. Claim 31) , a valve assembly R034 comprising a ring inserted into the hole of the cylinder head and having a length dimension corresponding to the degree of load reduction to be applied to the compressor; In the valve device described above, a slotted hole is formed in the end face of the cylinder head opposite to the compression chamber, and the carpenter also has a large inner diameter, and the ring is fitted into the slotted hole. Combined with 9 flanges?Equipped with 0 valve devices