JPS6138176A - Fluid pressure type compressor and fluid pressure control-power device of said compressor - 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 0) Industrial Application Field The present invention relates to a hydraulically driven compressor with infinitely variable capacity control for increasing the pressure of gaseous substances and Fluid pressure control for power plants.

←) Prior Art All of the prior art compressors for compressing gaseous substances (eg, air, nitrogen, or methane) suffer from one important drawback. Such prior art compressors do not provide capacity control that can be infinitely varied according to proportionally varied horsepower requirements. Such prior art compressors have attempted to alleviate this drawback by utilizing various capacity control devices such as unload valves or variable or constant volume pockets. These types of capacity control devices have limited range. The unload valve provides large capacity changes. A compressor driven by a reciprocating engine or turbine provides smooth capacity control over a portion of the engine or turbine's speed range, but typically the engine or turbine has no power when the engine or turbine speed drops below 50% of maximum speed. Cannot be used to operate the compressor. At speeds below 50 inches, these units must use a bypass valve to bypass excess capacity that is not needed. This method is significantly ineffective since the required horsepower does not change. This ineffectiveness is even more of a factor for constant speed compressors that are not fitted with unload valves or pockets.

e→Problem to be Solved by the Invention In situations such as when a compressor is used to compress and increase the pressure of natural gas flowing from a well head, The conditions of the gas flow can vary over a wide range. When a small volume of flowing gas enters the compressor, the compressor must operate at a very low speed in order to act on the natural gas to increase its pressure to the desired height. On the other hand, if a large volume of natural gas flows naturally from the head of the well, this compressor will be very quick to compress the large volume of natural gas to the desired high pressure. must operate. As such, it is highly desirable to have a compressor that can operate at infinitely variable speeds so that it can operate over a wide range of incoming gas flow conditions.

Other disadvantages associated with prior art compressors are that these compressors are significantly more complex in design and manufacture, thus increasing the costs associated with the manufacture and maintenance of such compressors. That's what I'm doing.

Particularly in the case of compressors utilized in remote wellheads, it is important that the compressor be easily serviceable and repairable. Furthermore, many prior art compressors provide the compression mechanism with cooling provided by a water jacket. Thus, this type of compressor requires a water source or a closed cooling system to dissipate the heat produced by the compression of the gaseous material. This type of water source may not be available in many remote locations. Moreover, this type of compressor requires additional components such as a water pump, which is amenable to maintenance problems.

Therefore, prior to the development of the present invention, it was possible to provide infinitely variable capacity control according to proportionately variable horsepower requirements; be efficient and economical in design; and be easy to care for and repair. There has never been a hydraulically driven compressor or a hydraulic control-power device for such a compressor that is easy; and does not require water cooling. Therefore, in this field of technology, there is a need to provide infinitely variable capacity control; to be effectively and economically controlled; to be easily and easily repaired and maintained; and to be air-cooled, hydraulically There is a need for a driven compressor and a hydraulic control-power plant for the compressor.

According to the invention, the above-mentioned advantages are achieved by means of a hydraulically driven compressor and a hydraulic control-power unit for the compressor. The present invention comprises a tenth retracting piston and a compression cylinder for initially compressing a gaseous substance;
a second double-acting piston and compression cylinder for additionally compressing the gaseous substance; R disposed between the first and second double-acting piston and cylinder, the piston y! l-first
and a hydraulically driven piston and cylinder disposed on a common elongated piston rod with a second double-acting piston: transferring compressed gaseous material from the first piston and compression cylinder to the second piston. and a first piping for transferring the compressed gaseous material to the compression cylinder; piping for transferring the compressed gaseous material from the second piston and the compression cylinder to the exit orifice; and for cooling the compressed gaseous material. first and second cooling coils associated with the first and second piping, respectively; a device for forcing air onto the first and second cooling coils; and a second piston and compression cylinder, a power piston and cylinder, first and second piping,
and air forcing devices are all arranged in the air cooling duct for the cooling of these devices, and the proportionally variable power demand for the Vc first and second pistons and compression cylinders. A device for providing infinitely variable capacity control according to It includes a variable displacement hydraulic pump system for hydraulically powered piston and cylinder operation so as to be operated over a range of .

Other features of the invention include an air forcing device or blower and a hydraulic prime mover for the blower, the prime mover including a pressure regulating valve and an associated pressure compensated flow control valve. , and the flow control valve is associated with and disposed between the variable displacement wave body pressure pump and the prime mover, so that the blower operates at a constant speed so that the first and second
cooling coils, first and second pistons and cylinders, and hydraulic power pistons and cylinders, and venting accumulated gaseous material from an air cooling duct. Yet another feature of the invention is that a cooling chamber is provided between the hydraulic power piston and cylinder and each first and second piston and cylinder, each cooling chamber displacing a portion of the piston. and includes a device for surrounding and directing the air flow from the air forcing device onto the piston rod.

Yet another feature of the invention is that the first and second pistons and compression cylinders and the hydraulic power piston and cylinder are disposed on the mounting plate by two mounting bolts, whereby the mounting The transmission of stress forces from the plate to the compression cylinder and the power cylinder is significantly reduced. Yet another feature of the invention is that first and second pistons are screwed onto said piston rod in a first direction and screwed onto said piston rod in a second opposite direction. The piston rod is fixed to the piston rod by a fixed member.

The invention further provides a compressor for gaseous substances having first and second double acting pistons and compression cylinders and reciprocating hydraulic power pistons and cylinders for actuating the first and second pistons. Fluid pressure control for - a variable displacement fluid pressure pump for providing hydraulic fluid to said power piston and cylinder to reciprocate said power piston within its cylinder in a power plant; a shuttle valve for alternating the flow of hydraulic fluid into and out of the ends of the power piston cylinder; a cam-actuated spring-loaded check valve associated with each end of the power piston cylinder; check valves actuated by reciprocating motion of said power piston to discharge hydraulic fluid from respective ends; discharge of hydraulic fluid through one of said cam actuated spring loaded check valves; a pilot valve for actuating the shuttle valve in response to a pressure difference generated by the pump; a reservoir for hydraulic fluid; and a reservoir for controlling the reciprocating motion of the piston so as to vary the speed of the reciprocating motion of the piston as the displacement of the pump is varied; , a pump, a shuttle valve, a check valve, a pilot valve, and hydraulic fluid piping operatively interconnecting the reservoir.

Yet another feature of the invention is that a flow control valve throttles hydraulic fluid flowing from the pilot valve to either end of the shuttlecock to control the rate of reciprocating motion of the shuttlecock; 5 can be operatively associated with each end of the front Hd shuttle valve so that the hydraulic impulses produced by the rapidly reciprocating shuttle valve are controlled. A unique feature of the present invention is that a ball check valve and a fluid control valve are each operatively associated with a needle valve to create a pressure differential for reciprocating the pilot valve. This is something that can be done.

A pressure regulator is installed to adjust the pump discharge pressure to a relatively low level for the control system. Adjustment of the pressure in this control system ensures that the response times for all needle valves in the system are uniform so that the pressure differential across the needle valves in the control system remains constant regardless of pump pressure. be treated like

An additional feature of the invention is that a pressure relief valve can be operatively associated with the pump so that excessive pressure built up within the piping or any compression cylinder can be safely relieved. It is.

Another feature of the invention is that a pressure compensated flow control valve and distribution block are operatively connected to the pump and piping to provide lubricating hydraulic fluid to the piston rod and compression cylinder for the double acting piston. It is something that can be related to.

The hydraulically driven compressor of the present invention and the hydraulic control-power plant for the compressor are designed to meet directly related horsepower requirements when compared to prior art compressors. Provides infinitely variable capacity control; Efficiently and economically constructed; Easily repaired and maintained;
It also has the advantage of cooling various components of the compressor with air.

(e) Examples and Effects Although the present invention will be described below in connection with preferred embodiments, it is not intended that the invention be limited to those embodiments. On the contrary, it is intended to cover all changes, modifications, and equivalents as may come within the scope and spirit of the claims appended hereto.

FIG. 1 shows a hydraulically driven compressor 51 of the present invention for increasing the pressure of gaseous substances, such as air, nitrogen or methane.

Compressor 51 generally includes a first double-acting piston 5 that initially compresses a gaseous substance (not shown) as described below.
2 and compression cylinder 53; a second double-acting piston 54 and compression cylinder 5 providing a second stage of compression as described below.
5; and a hydraulic power piston 56 and cylinder 57 disposed between first and second double-acting pistons 52.54 and cylinders 53.55. As shown in FIG.
and hydraulic power pistons 56 are each mounted on a common elongated piston rod 58, which extends from cylinder 53.5 to cylinder 53.5.
5.57 longitudinal axes are axially aligned. The above-described components of compressor 51 may be manufactured from any suitable material having the required strength properties; however, for ease of assembly and economical manufacture, preferably
The cylinders 53, 55, and 57 are preferably manufactured from commercially available drawn man P-rel steel tubing, which is readily and economically available. As is customary in two-stage compressor designs, the diameter of the second compression cylinder 55 is larger than that of the first compression cylinder 5 to provide the second stage of compression of the gaseous material.
The diameter is smaller than 3. Of course, if desired, the diameter of the second compression cylinder 55 may be the same as the first compression cylinder 53 to provide a single stage compressor. Appropriate piping connections are made so that the incoming gaseous material simultaneously enters both cylinders via a shared inlet manifold and the compressed gas exits into a shared discharge manifold and enters the cooling system described below. will be provided. Similarly, up to four stages of compression could be obtained using a cylinder with a single stasol design.

1, the compressor 51 of the present invention also generally transfers compressed gas to a first piston and a compression cylinder 5.
2.53 to second piston and compression cylinder 54.55
It includes a first piping 59 (shown in dotted line for illustration purposes) for transferring to. A second piping 60 (also shown as a dot for illustration purposes) transfers the compressed gas from the second piston and compression cylinder 54,55 to an exit orifice, generally designated 61. It is deployed for. This gaseous material, after being brought to pressure la and increased pressure, exits at the exit orifice 61 to the compressor 51' (at whatever location and/or location it is desired to be used). , for example to a storage tank, or to a pipeline or the like.

In FIG. 1, first and second pipes 59, 60 are associated with the first and second pipes 59, 60 to cool the compressed gaseous material.
It can be seen that cooling coils 62 and 63 are present. As illustrated in FIG. 1, a first cooling coil or intercooler 62 is disposed intermediate the ends of the first pipe 590, and a second cooling coil or postcooler 63 is located between the ends of the first pipe 590.
The pipe 600 is placed in the middle between both ends. Compressor 51
further includes a device 64 for forcing air past the first and second cooling coils 6263. Preferably, the strong side device 64 includes a plurality of blower blades 65 rotated by a fluid pressure source motor 66 . Additional cooling coils can be provided if required as well as a thermostat to control the operation of the blower depending on the ambient temperature. As illustrated in FIG.
．． 60, the first and second cooling coils 62, 63 and the air forcing device 64 are preferably arranged in an air cooling duct 67 which preferably extends the entire length of the compressor 51. The air cooling duct 67 can be manufactured from any suitable material, such as sheet metal, and the cooling coil 6
2 and 63 and other components of compressor 51 so long as they serve to confine the flow of air produced by air forcing device 64;
For example, it can have a circular, U-shaped, or rectangular shape. In the event of a leak within the compressor 51, a constant flow of air from the blower blades or an air cooling duct 67 to evacuate the accumulated gas also protects the various components of the compressor from natural forces and adverse environmental conditions. It also has the function of Thus, once the hydraulic prime mover 66 of the air forcing device 64 is supplied with hydraulic fluid, the blower blades 65 are caused to rotate and draw air ff into the air cooling duct 67, and this air is thus transferred to all other parts of the compressor 51. It not only passes through the air cooling duct 61 from right to left in FIG. 1, but also crosses cooling coils 62 and 63.

(Thus, the first stage piston and compression cylinder 52゜53
The gas compressed inside passes through the pipe 59 to the intermediate cooling a62.
As the gas flows through intercooler 62 and postcooler 63, the flow of air from vanes 65 dissipates the heat in the gas produced by the compression of the gas.

Cooling coils for the hydraulic oil may also be installed in the air cooling duct 67 to reduce the operating temperature of the hydraulic oil by J% if required.

It can be seen in FIGS. 1 and 2 that the compressor 51 is provided with cooling chambers 68 and 69. In particular, in FIG. 2, the cooling chamber 68 is connected to the first stage piston and cylinder
and the hydraulic power piston and cylinder 56, 57; and a cooling chamber 69 is located between the hydraulic power piston and cylinder 156, 57 and the second stage piston and cylinder 54, 55. . Cooling room 68.6
9 each surround a portion of the piston rod 58 and include a device for directing air flow from the air forcing device 64 onto the piston rod. Preferably, a device 70 for directing the total airflow.
Preferably, the air is directed from the blower vanes 65 inwardly into the cooling chambers 68 and 69 into flow elbows or ducts 71'. The valleys of the cooling chambers 68,69 contain a device for directing the entire airflow from the air forcing device [1'64] onto the piston rod. Preferably, an air flow directing device 170 directs air from blower blades 65 to cool chambers 68 and 6.
It is preferred to include a flowing elbow or duct) 71Y inwardly into the 9. The valleys of the cooling chambers 68,69 have a plurality of suitable openings (not shown) for venting air from the ducts 71 outwardly from the cooling chambers 68,69. (Thus, the additional heat generated during the operation of the compressor 51 is transferred to the cooling chamber 68.
．． 69 will be dissipated by convection.

Furthermore, in FIGS. 1 and 2, each cylinder 53
．． 55 and 57 have first and second cylinder header members. First stage cylinder 53 includes $1 and second header part 72,73; hydraulic cylinder 57
are included in the first and second header members 74,75;
The second stage compression cylinder 55 also includes first and second header members 76,77. One set of each header member and compression cylinder 72.73.53; 74°75.57
; and 76.77.55 is a plurality of elongated tie rods (
(not shown for illustrative purposes) allow the various components of compressor 51 to be easily assembled and disassembled for maintenance. As shown in detail in FIG. 2, the cylinder ends of the valleys are sealed to their respective header members by O-ring seals 50 that engage the inner surface of each cylinder. Therefore, the amount of surface area of each header member on which the gas pressure acts is reduced, thereby reducing the amount of surface area of each header member in each pair of header members, such as the L connecting tie opening, HH1, etc.
11 Ding + Darkness Sword 1f 1x Fake Gauze Mizuhiki Sue In Figures 1 and 2, cooling chambers 68 and 69 are formed by outer housing members 78 and 78' and header members 79 and 79'. It will become clear. The hawasings 78, 78' can have any cross-sectional shape. Preferably, however, the housing member 78, 78' has a circular cross-sectional shape. The housing member 78 has a K groove 8 as shown in FIG. 2, for example.
0, the receiver is received into the header member 13. The construction of the housing member 18' and the header member 79' is the same as previously described with respect to the housing member 78 and the header member 79. It will further be seen in FIGS. 1 and 2 that the header members 79, 79' are attached to the header members 74, 75 of the power cylinder 5T by, for example, a plurality of bolts or tie rods 82.

1 and 2, all of the aforementioned components of the compressor 51 rest on a mounting plate 84 on a ground surface 84 or on any other suitable structure, such as a portapu-type skid.
You can see that it is placed on 3. The air forcing device 64 may be rigidly secured to the mounting plate 83 by vertical struts 85, for example, and the cooling coils 62,63 may be secured to the mounting plate 83 in any conventional manner. A member 86 is provided. First stage piston and cylinder 52
．． 53, the second stage piston and cylinder 54°55, and the hydraulic power piston and cylinder 56°57 are in the cooling chamber 68
．． 7 langes 89 and 90 are attached to the housing member γ8° 78' of 69, and the receivers are received in the mounting lugs 91 and 92 fixed to the mounting plate 83.
．． It is arranged on the mounting plate 83 via two poles 87 and 88v passing through the mounting plate 90. Therefore, the compressor 5
The compressor component 1 has a two-point mounting system, whereby the transmission of stress forces from the mounting plate 83 to the compression cylinder 53.55 and the power cylinder 57 is significantly reduced. This two-point mounting system allows some flexure and movement of the various components of compressor 51 with respect to each other that is not detrimental to the operation of compressor 51, and also allows the various components of compressor 51 to be attached to mounting plate 83. To provide an extremely simple, economical and effective system for mounting on.

As shown in FIG. 1 and particularly in FIG. 2, both the first stage cylinder 53 and the second stage cylinder 55 are sealed at the point where the piston rod 58 enters the cylinders 53 and 55. . A rod backing 93 is provided within the header member 73 and the same bale backing 94 is provided within the header member 76.
provided within. The valleys of the header parts 73 and 76 have lubrication connecting passages or ducts 95,96 which also support the piston rod 58 and the rod backings 93 and 94 to lubricate the backing housing. and 94 for fluid communication.

The transmission of hydrostatic lubricating fluid through the ducts 95, 96 will be discussed below with respect to FIG.

With reference to FIG. 1, the construction of the first and second stage pistons 52 and 54 will be described. Pistons 52 and 54 are secured to the inside of cylinders 53 and 55 by a plurality of polytetrafluoroethylene (PTF'E) piston rings 97 mounted in grooves in the outer surfaces of these pistons. Sealed against the surface. P
The TFE ring 9γ supports the pistons 52 and 54 within the cylinder 53°55, thereby allowing the piston 52.
The outer surface of 54 is cut away from contacting the inner surface of cylinder 53.55. Pistons 52 and 54 can therefore be reciprocated within cylinder 53.55 without lubrication being provided to cylinder 53.55.

The compressor 51 has first and second stage pistons and cylinders 52.
- Lubricating connections 99 for cylinder 53 and 100 for cylinder 55 when used to compress and build up the pressure of some type of wet gaseous substance in which lubrication is desired. Hydraulic lubricating oil can be provided by each of the above. Suitable piping (not shown) is provided to transmit hydraulic fluid to the lubrication connection 99.100 as described below with respect to FIG.

One of the important safety features of the present invention is that piston 52.
A wire connection is illustrated and is rigidly secured to piston rod 58 by piston 541 (same as that utilized).

Preferably, the threaded connection 101 has a first threading direction, preferably with a right-handed thread.

Fixing member or socket head cap screw 102
engages the end of piston rod 58 and is screwed into the outer surface of piston 52. The fixing member 102 is screwed into the piston rod 58 through the piston 52 in a second opposite direction. Preferably, the fixing member 102 and its mating surface within the piston 52 have left-handed threads. Therefore, the possibility that vibrational forces will cause the piston 52,54 to become uncoupled from the piston rod 58 is significantly reduced. The safety aspect of the compressor 51 is greatly enhanced since if the piston were to become loose from the piston rod 58, it would cause severe harm to the compressor 51 and/or persons in the vicinity of the compressor.

Similarly, hydraulic power piston 56 is connected to pistons 52 and 5.
4, a suitable seal 103 is disposed within the groove provided on the outer surface of the piston 56. A seal for the power cylinder 57 in which the piston rod 58 is located within the fitting members 74 and 75 when no lubricating fluid is delivered through the lubricating connections 95 and 96 for the piston rod backings 93 and 94. It should be noted that the hydraulic fluid left on the piston rod 58 provides a suitable amount of lubrication during reciprocation through the piston rod 104.

1 and 2, the cylinders 56, 57 of the compressor 51 are connected to the power cylinder header members 74, 75.
There is provided an inlet 105 for the supply and discharge of hydraulic fluid located within. As the power piston 56 reciprocates within the cylinder 5T, the pawl type check valves 106 and 107 are opened alternately.

Referring specifically to FIG. 2, power piston 56 includes tubular camming members 108 and 108' located on either side of piston 56. The camming member 108 will engage and open the cam actuated spring loaded ball check valve 106 as the piston 56 reciprocates within the cylinder 5γ. Also, the cam action member 108'
Similarly, as will be detailed later, the other check valve 107
will engage and release it. The opening of the cam-operated check valves 106, 107 creates a pressure differential that reciprocates the pilot valve 133, as will be described later.

1 and 4, flow diagrams for gaseous substances to be compressed are detailed. The gaseous material to be compressed, coming from, for example, a well head, storage tank, etc., will first pass through an optional scrubber unit 109, as illustrated in FIG. From the scrubber unit 109, this gas passes through piping (schematically shown as 110 in FIG. 4) and enters the first compressor stage cylinder 53 via an inlet manifold 111. However, the inlet manifold 111 distributes gas through piping 112 to two inlet ball check valves 113, 114 located within the header member 72, 74. As will be discussed below, the hydraulic power piston 56 With the reciprocation of the piston 5
2 are reciprocated within the first stage cylinder 53, thus alternately sucking gas through the inlet check valves 113, 114 and compressing the gas within the cylinder 53 on either side of the piston 520. Next, this compressed gas is similarly transferred to the header member 72.
It is discharged from the first cylinder 53 through a discharge check valve 115.1'16 mounted in 73. Discharge check valves 115, 116 feed pipe 117 leading to discharge manifold 118 and first pipe 59 as described above. The compressed gas then enters another optional scrubber unit 119 through the intercooler 62 and through the first piping as shown in FIG. Gas comes first
After being compressed within the stage, cooled, and then optionally flushed, the gas enters the second stage inlet manifold 1201 through the first line 59, passes through line 121 and then into the second stage inlet manifold 1201. Passing through the inlet pole check valves 122, 123, this gas is thus compressed in the second stage cylinder 55 as it is done in the first stage cylinder 53. Next, the gas is the second
It is discharged through stage discharge check valves 124 and 125 into piping 126 and discharge manifold 12γ. The compressed gas then passes through the second line 60 as previously described into the aftercooler 63 and then to the outlet orifice 61. Top gap bottle 1 in which at least one of the compression cylinders 53,55 is associated with a pipe tap threaded opening, such as the one shown at 128, in the header 71
29, whereby the second stage compressor cylinder 55
It should be noted that the zero top gap volume can be made variable to provide a balanced compression ratio between the first and second compression cylinders 53,55. The header 12 of the first stage compression cylinder 53 can also be provided with a similar pipe tap threaded opening as shown at 128 and provided with a similar top clearance bottle 129 in this opening. should also be noted.

Referring now to FIG. 3, fluid pressure control for compressor 51 -
Explain the power plant. First, the components to be described below, with the exception of the hydraulic power piston and cylinder 56, 57, may be placed in the air cooling duct 67 if space permits, or in any suitable base member or slide plate. It should be noted that the upper compressor 51 may be located adjacent to it. Generally, this hydraulic control-power plant 103 includes the following components: a shuttle valve 132; a cam-actuated spring-loaded check valve 106, as previously described;
107; Hydraulic power piston and cylinder 5 as described above
6.57; Pilot valve 133; Hydraulic fluid reservoir 134
flow control valves 135, 136 operatively associated with each end of shuttle valve 132; needle valves 131-14;
0; Ball type check valve 141; Manual bypass valve 142; Relief valve 143; Prada type accumulator 144; Pressure compensated control valves 145, 146; Fluid pressure distribution block 1
4T; hydraulic feed inlet 105 as described above; hydraulic fluid filter 148, 149; Prada type accumulator 15
6; and a back pressure control valve 157. pump 1
31, the shuttle valve 132, the check valves 106, 107, the pilot valve 133, the reservoir 134, and other components of the fluid pressure control-power plant 130, as will be described in greater detail hereinafter, 51 are operationally associated with each other; Hydraulic fluid piping as illustrated throughout FIG. 6 is further provided.

Hydraulic oil 150 is stored in reservoir 134 and is sucked into the pump through suction screen 148 and piping 151 when variable displacement pump 131 is activated or started. Suction screen 148 serves to prevent any impurities from entering hydraulic control and power plant 130 . Pump 131 is pump actuator head 1
531 is controlled by a control signal applied. Pump 131 is initially stopped stroking at a flow rate of zero by discharging control signal 152 which acts on actuator head 153. Control signal 15 after a certain period of warm-up operation
2 is returned to pump actuator head 153 and thus pump 131 increases its stroke in response to an increasing control signal acting on actuator head 153. Accordingly, the flow of hydraulic fluid 130 through the device 130 begins and the pressure of the hydraulic fluid 150 throughout the device 130 reaches the first and second stages due to the presence of gaseous material in the compression cylinder 53. The pressure increases to the level necessary to overcome the pressure loads acting on the second stage pistons 52,54. It should be noted that increasing the control or pressure signal 152 to the pump actuator head 153 increases the speed of circulation or reciprocation. This increased speed, in turn, increases the capacity of compressor 51, thus compressing the increased volume of incoming gas with the associated increase in horsepower required. Similarly, Bonzo actuator P15
By reducing the pressure or control signal 152 acting on 3, the speed of the hydraulic control-power plant 130 is reduced;
Thus, with the associated increase in horsepower required, the speed of the compressor is reduced to accommodate the reduced volume or capacity of the incoming gas. Therefore, the fluid pressure control-power device 130 of the present invention includes the compressor 51
Compressor 5 to provide infinitely variable capacity control of
1 to operate over an infinitely variable speed range. If the flow and pressure conditions arriving into the first stage compressor change, to compensate for the changed arrival pressure and flow conditions of the gaseous material, simply change the control signal to the variable displacement pump 131. That's fine. The power source for variable displacement pump 131 may be of any conventional type, including a constant speed motor, a reciprocating engine, or any other suitable rotary power source. In the case of a variable displacement pump, the speed of its power source remains constant, but the horsepower required to operate the pump can vary in proportion to the flow rate of the pump. Thus, when this compressor 51 is operated, for example, at a lower capacity, for gas flowing under reduced flow conditions, the horsepower required from the power source is similarly reduced proportionally, so that the energy is saved.

Further, in FIG. 6, hydraulic fluid 150 exits variable displacement pump 131 at an outlet orifice, such as shown at 154, and enters ball check valve 141.
Or it can be seen that it passes through other suitable valves. The ball check valve 141 prevents hydraulic fluid pressure from backing up the pump 131 when the pump 131 is shut off, and also reverses the flow of hydraulic fluid and drains the hydraulic fluid 150 within the pump 131. prevent. Pressure relief valve 143 is of conventional construction and protects all hydraulic components of system 130 from excessive pressure built up within hydraulic piping or compression cylinders 53.55, thereby preventing such excessive pressure. It should be noted that pressure build-up is safely relieved by relief valve 143. Furthermore, the pressure relief valve 143 allows the liquid substance to be compressed into the compression cylinder 53.
, 55 to pass through this without damage. It is not uncommon for pressurizers operating on natural gas at the wellhead to force liquid from the wellhead into the gas stream. This situation is commonly referred to as "liquid slugging" and is also known as
If such incoming liquid slug enters the compression cylinder, it is likely that it will cause significant damage to the compressor cylinder due to the built-up pressure.

As illustrated in FIG. and 107 typically tubular camming member 10
8, 108', the zero-force actuating member 108' is maintained in the closed position until it is opened by the ball-type check valve 107.
Hydraulic power piston 56 moves to the right toward ball check valve 107 until it opens to release hydraulic fluid pressure through hydraulic fluid delivery conduit 105 and header member 75 . Thus, by opening the ball type check valve 101,
Hydraulic fluid is supplied to the pipe 1 at the end of the pilot valve 133.
55 and into storage tank 134. This discharge of hydraulic fluid creates a pressure differential across the four-way pilot valve 133, which is then stroked to apply system pressure to the opposite end of the four-way shuttle valve 1320. At the same time, the previously pressurized end of the shuttle valve 132 is discharged through the pilot valve 133 to the reservoir 134 as shown in FIG. 83. This shift of the shuttle valve causes hydraulic fluid 150 to be alternately applied to and removed from the hydraulic fluid delivery inlet 105 provided in the header 74, 75, thereby causing the power piston 56 to reciprocate within the cylinder 57. I am forced to do it. The flow control valves 135 and 136 are the pilot valve 13
3 to the end of the shuttle valve 132.
50 controls the speed at which this shuttle valve 132 moves, so that the fluid pressure flow control valve created by too rapid switching of the shuttle valve is controlled by the device 13.
It should be noted that it can also be operatively associated with both ends of the pilot valve 133 to further control the switching response of the zero fluid pressure component. Pilot valve 13
3. Shuttle valve 132 and flow control valves 135, 13
It should be noted that No. 6 is the most commercially available valve. The oil discharged from the four-way shuttle valve 132 is discharged in a pulsating manner. These pulsations, which can be detrimental to the components of the hydraulic system, are effectively damped using the accumulator 156 in conjunction with the back pressure control valve 157, thus ensuring long system component life.

The four-way pilot valve 133 incorporates a mechanical catch or detent that secures the pilot "valve spool" 133 in position in the event of system flow interruption. Without this feature, pilot valve spool 133 would be able to seek a neutral position within the valve body and as a result compressor 51 would not be able to be started.

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The valve 146 can also be operatively associated with the pump 131 to meter and regulate hydraulic fluid 150 to the distribution block 147. Thus, distribution block 147 can, if desired,
Hydraulic fluid 15 to first and second stage cylinder lubrication connections 99, 100 and rod backing slide devices 95,96
Weigh the exact volume of 0. A manual bypass valve 142 may be provided to manually relieve pressure within pump 131 if desired. A bladder type accumulator 144 may also be operatively associated with pump 131 and device 130 to reduce system pulsations or pressure shocks when shuttle valve 132 switches. Bladder type accumulator 144 serves to store and store hydraulic energy in the event of switching of throttle valve 132.

As previously mentioned, the prime mover 66 for the blower blades 65 is hydraulically operated and its speed is controlled by a pressure compensated flow control valve 145t.

Once the valve 145 is set to the desired pressure rating, the speed of the blower prime mover 66, and thus the rotation of the blower blades 65, remains constant even as the pressure of the hydraulic system within the apparatus 130 changes. Let's see how to maintain it. In this regard, in order to control changing temperature conditions caused by increased ambient temperature conditions at the location of the compressor 51 or increased temperature carried over by the gaseous material arriving at the compressor 51. It should be noted that the state can be varied by adjusting the pressure compensated control valve 145.

Pall type check valves 106 and 107 and flow control valve 135
and 136 are each a needle valve 137-14 for varying the flow rate to said valve to vary the response time of said valve.
0. It is understood by those of ordinary skill in the art that the two compressors 51 of the present invention can be connected together in series with suitable piping connections between them to provide four stages of compressors. would be easily obvious.

FIG. 5 shows an embodiment similar to that of FIG. 6, but with a somewhat slimmer design. In this example,
In place of the return filter 149 of the embodiment of FIG. 6, a filter 149' is arranged in the suction line. Filter 149' filters extremely small molecules to prevent them from entering pump 131, thereby extending the life of the pump.

Also, in FIG. 5, a pressure regulating valve 159 is provided as part of the fluid pressure control/power unit 130, and a main shuttle valve 132 directs the main oil flow to the inlet 105 in the main cylinder 156. A check valve 106 is provided to prevent backflow pressure surges in this control device when it is moved quickly from side to side.
107.

The pressure provided by the regulated fluid pressure control system and pressure regulator 159 is controlled by a cam actuated spring loaded check valve 1
06. '107 and needle valve 13γ.

138, thereby normally operating the check valve 106°10
7 is maintained in the closed position by being opened by tubular camming members 108, 108'. The prime mover for the blower blades 65 also has speed control by a control system, and the pressure regulator also controls the control system pilot pressure. Once the pressure regulating valve 159 is set to the desired pressure rating f, the speed of the blower prime mover 66 will remain constant even if the system fluid pressure within the device 130 changes.

It is understood that this invention is not limited to the precise details of construction, operation, precise materials or embodiments disclosed, as obvious modifications and alterations will be apparent to those skilled in the art. It should be. For example, intercoolers and postcoolers and forced air devices may be utilized as units mounted on large separate slides, even if additional cooling of the compressed gas is required. can be done. Accordingly, the invention should be limited only by the scope of the appended claims.

[Brief explanation of drawings]

1 is a partial cross-sectional view along the longitudinal axis of a compressor according to the invention; FIG. 2 is a partial cross-sectional view according to the invention;
Full view of the house σ) City city Lγ ★) - Connor,
7t+ Jif 邊1 f-xiang Q-fh Taipei sectional view; FIG. 6 is a schematic fluid pressure flow diagram of a fluid pressure control-power device as an example according to the present invention; FIG. 4 is a diagram showing the flow diagram of the present invention a schematic flow diagram of the gaseous substance to be compressed according to;
FIG. 5 is a schematic diagram similar to FIG. 6 illustrating an alternative embodiment of a hydraulic control-power system according to the present invention. 51... Hydraulically driven compressor, 52...
First double-acting piston; 53... compression cylinder; 54.
...Second double-acting piston; 55...Compression cylinder; 5
6. Fluid pressure power piston; 57. Cylinder; 58.
...Shared elongated piston rod; 59...First piping;
60... Second piping; 61... Outlet orifice; 6
2゜63...First and second cooling coils; 64...Air forcing device; 65...Blower blades &! 66... Fluid pressure prime mover; 67... Air cooling duct OES, SS.
... Cooling chamber; 70... Air flow guide device; 71... Duct; 72° γ3... First and second header part; γ
4. γ5...First and second header member; 76.7γ
...First and second header members; γ8, 78'...
・Outer housing member, 79, 19'... Header part; 80... Groove; 81... Header part; 82.
... Bolt or Quirod: 83 ... Mounting plate; 84
... Ground surface; 85 ... Vertical support; 86 ... Base member; 87, 88 ... Port: 89.90 ... Flange; 91, 92 ... Mounting lug; 93. 94...
・Rod backing; 95, 96...Duct; 97...
Piston ring; 99,100...Lubrication connection part; 10
1... Threaded connection part; 102... Fixing member; 103... Seal; 104... Seal; 10
5...Discharge port; 106,107・Ball type check valve-
; 108, 108'... tubular cam action member; 1
09... prior art scrubber units); 110...
・Piping; 111...Inlet manifold; 112...Piping; 113.114...Ball type check valve; 115, 11
6...Discharge check valve; 117...Piping;118...
・Discharge manifold; 119... Flapper unit; 120... Second stage Roman manifold; 121... Piping; 122° 123... Second inlet ball type check valve; 124, 125...・Second stage discharge check valve; 126
...Piping;127...1Ltlfl manifold;1
28... Pipe tap screw hole; 129... Top gap bottle; 131... Variable response type fluid pressure pump: 132...
Shuttle valve; 133・Repilot valve; 134...
Hydraulic fluid storage tank; 135, 136...flow control valve; 13
7-140... Needle valve; 141... Ball type check valve; 142... Manual bypass valve; 143... Relief valve; 144... Plug type accumulator; 145,1
46...Pressure-compensated control valve; 147...Fluid pressure distribution block; 148.149...Fluid pressure fluid filter; 150 River fluid pressure oil: 151...Piping; 15
2... Control signal; 153... Pump actuator head;
156... Plug type accumulator; 157... Back pressure control valve;

Claims (10)

[Claims] (1) A compressor driven by fluid pressure for increasing the pressure of a gaseous substance, comprising a first double-acting piston and a compression cylinder for initially compressing the gaseous substance; adding the gaseous substance; a second double-acting piston and a compression cylinder for compressing the piston; a second double-acting piston and a compression cylinder disposed between the first and second double-acting pistons and cylinders for compressing the piston; a hydraulically driven piston and cylinder disposed on an elongated piston rod; a first piston and cylinder for transferring compressed gaseous material from the first piston and compression cylinder to the second piston and compression cylinder; piping; second piping for transferring the compressed gaseous substance from the second piston and compression cylinder to the exit orifice; first and second piping, respectively, for cooling the compressed gaseous substance; in a compressor comprising: first and second cooling coils associated with piping; and a device for forcing air over the first and second cooling coils; the piston and compression cylinder, the power piston and cylinder, the first and second piping, and the air forcing device are all disposed within an air cooling duct for cooling of these devices; and a device for providing infinitely variable capacity control according to proportionally variable power requirements for the first and second pistons and compression cylinders; A variable displacement hydraulic pump arrangement for actuating hydraulic power pistons and cylinders such that the pistons and compression cylinders are actuated over a range from 0 to 100% of capacity according to proportionally variable power demands. A compressor characterized by: (2) In the compressor according to claim 1, the first and second pistons and compression cylinders and the hydraulic power piston and cylinder are arranged on a mounting plate by two mounting bolts. the first and second pistons are screwed into the piston rod in a first direction, thereby significantly reducing the transmission of stress forces from the mounting plate to the compression cylinder and the power cylinder; A compressor characterized in that the compressor is fixed to the piston rod by a fixing member mounted on the piston rod and screwed into the piston rod in a second opposite direction. (3) A compressor according to claim 1, wherein the air forcing device includes a blower and a hydraulic prime mover for the blower, the prime mover having an associated pressure compensating flow control valve. and associated with and disposed between the variable displacement hydraulic pump and the prime mover, the blower operating at a constant speed, first and second cooling coils;
Similarly, a hydraulic system cooler installed in the duct cools the first and second pistons and cylinders, and the hydraulic power piston and cylinder, and also cools gaseous substances accumulated from the air cooling duct. A compressor that is unique in that it blows out. (4) In the compressor according to claim 1, the first compression cylinder is caused by the fact that a liquid rather than a gaseous substance enters one of the first and second compression cylinders.
or a hydraulic variable displacement pump and a pressure relief valve arrangement associated with the first and second compression cylinders to prevent excessive pressure buildup within the second compression cylinder; A compressor characterized in that liquid is allowed to pass through this valve arrangement at a safe operating pressure level. (5) The compressor according to claim 1, wherein a cooling chamber is provided between the fluid pressure power piston and the cylinder, and each of the first and second pistons and cylinders; A compressor characterized in that a chamber surrounds a portion of the piston rod and includes a device for directing a flow of air from the air forcing device onto the piston rod. (6) for a compressor for gaseous substances, having first and second double-acting pistons and compression cylinders, and a reciprocating hydraulic power piston and cylinder for actuating the first and second pistons; Hydraulic control of - in a power device, a variable displacement hydraulic pump for providing hydraulic fluid to the power piston and cylinder to cause the piston to reciprocate within its cylinder; a shuttle valve for alternating the flow of hydraulic fluid into and out of the ends of the piston cylinder; a cam-actuated, spring-loaded check valve associated with each end of the power piston cylinder; check valves actuated by reciprocating motion of said power piston to discharge hydraulic fluid from respective ends; discharge of hydraulic fluid through one of said cam actuated spring loaded check valves; a pilot valve for actuating the shuttle valve in response to a pressure difference generated by the piston; a reservoir for hydraulic fluid; and a reservoir for the hydraulic fluid so that the speed of the reciprocating motion of the piston can be varied when the displacement of the pump is varied; , a pump, a shuttle valve, a check valve, a pilot valve, and hydraulic fluid piping that operatively associates a reservoir with each other.
Power plant. (7) In the fluid pressure control power plant according to claim 6, the reciprocating speed of the shuttle valve is controlled and the fluid pressure shock generated by the shuttle valve reciprocating too quickly is controlled. a flow control valve arrangement operatively associated with each end of the shuttle valve to throttle hydraulic fluid flowing from the pilot valve to either end of the shuttle valve; A fluid pressure control-power device having the following characteristics. (8) A fluid pressure control-power device according to claim 6, wherein the pressure shock generated by the reciprocating movement of the shuttle valve is absorbed, and the pump energy is required to switch the shuttle valve. A fluid pressure control and power device characterized in that it has a bladder-type accumulator operatively associated with said pump and piping so that said fluid is accumulated for a period of time. (9) a hydraulically driven compressor for increasing the pressure of a gaseous substance, comprising a first double-acting piston and a compression cylinder for compressing the gaseous substance; a second double-acting piston and a compression cylinder; disposed between the first and second double-acting pistons and cylinders;
a hydraulically powered piston and cylinder disposed on an elongated piston rod sharing the piston with first and second double-acting pistons; compressed gaseous substance from the first and second pistons and the compression cylinder; piping for transferring to an exit orifice; cooling coils each associated with said piping for cooling the compressed gaseous material; and a device for forcing air over said cooling coils. , in a hydraulically driven compressor; the first and second pistons and compression cylinders, the power piston and cylinder, the piping;
The cooling coils and air forcing devices are all arranged in air cooling ducts for the cooling of these devices; and infinitely variable displacement control for the first and second pistons and compression cylinders. the displacement control device includes a variable displacement hydraulic pump for actuating the hydraulically powered pistons and cylinders, such that the first and second pistons and compression cylinders are proportionally powered; A compressor characterized in that the compressor is operated over a range from 0 to 100% of its respective capacity according to changes in capacity. (10) In the compressor according to claim 9,
The air forcing device includes an air blower and a hydraulic prime mover for the blower, the prime mover having an associated pressure regulating valve and associated with and associated with the variable displacement hydraulic pump and the prime mover. disposed between each other so that the blower operates at a constant speed to cool the first and second cooling coils, the first and second pistons and cylinders, and the hydraulic power piston and cylinder and to blow the air. A compressor characterized by blowing out accumulated gaseous substances from a cooling duct.