US3811795A - High pressure fluid intensifier and method - Google Patents

High pressure fluid intensifier and method Download PDF

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Publication number
US3811795A
US3811795A US00322956A US32295673A US3811795A US 3811795 A US3811795 A US 3811795A US 00322956 A US00322956 A US 00322956A US 32295673 A US32295673 A US 32295673A US 3811795 A US3811795 A US 3811795A
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Prior art keywords
working
valve means
control valve
shifting
pressure
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US00322956A
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English (en)
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J Olsen
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Flow Research Inc
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Flow Research Inc
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Priority to US00322956A priority Critical patent/US3811795A/en
Priority to CA189,213A priority patent/CA1006787A/en
Priority to GB44374A priority patent/GB1420424A/en
Priority to AU64259/74A priority patent/AU483161B2/en
Priority to ZA740112A priority patent/ZA74112B/xx
Priority to IL43965A priority patent/IL43965A/en
Priority to SE7400308A priority patent/SE398911B/xx
Priority to IN74/CAL/74A priority patent/IN141336B/en
Priority to DE2401341A priority patent/DE2401341C2/de
Priority to IT47665/74A priority patent/IT1008123B/it
Priority to NL7400433A priority patent/NL7400433A/xx
Priority to FR7400963A priority patent/FR2214051B1/fr
Priority to JP49006937A priority patent/JPS614997B2/ja
Priority to ZM7/74A priority patent/ZM774A1/xx
Application granted granted Critical
Publication of US3811795A publication Critical patent/US3811795A/en
Assigned to SEATTLE-FIRST NATIONAL BANK reassignment SEATTLE-FIRST NATIONAL BANK SECURITY INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: ADMAC, INC.
Anticipated expiration legal-status Critical
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/08—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid
    • F04B9/10—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
    • F03C1/00—Reciprocating-piston liquid engines
    • F03C1/08—Distributing valve-gear peculiar thereto
    • F03C1/10—Distributing valve-gear peculiar thereto actuated by piston or piston-rod
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B3/00—Intensifiers or fluid-pressure converters, e.g. pressure exchangers; Conveying pressure from one fluid system to another, without contact between the fluids

Definitions

  • HIGH PRESSURE FLUID INTENSIFIER AND METHOD BACKGROUND or THE INVENTION rapid reversal of the working piston so that there is no' significant interruption of the flow of high pressure output fluid.
  • Yet another problem in the prior art is that of alleviating pressure surges in the working fluid while the working piston is being reversed. Aside from these with manys'uch prior art devices is that of obtaining a operational problems, there are, especially when very 4 high pressures are used, safety considerations with respect to one of the hydraulic lines or other components breaking or rupturing.
  • a working cylinder in which a working piston is mounted for'reciprocating motion, the piston dividing the cylinder into first and second working chambers.
  • Two high pressure pistons are connected to the working piston. in a manner that reciprocation of the working piston causes a flow of high. pressure fluid to be procuced altemately from the two high pressure pistons.
  • the high pressure flow is directed through a discharge nozzle to produce a high velocity stream of water.
  • Tocause reciprocation of the working piston there is a control valve having first and second positions to deliver pressurized working fluid to, respectively, the first and second working chambers.
  • the control valve has a third intermediate position through which it passes in moving between its first and second positions.
  • pressurized working fluid is directed through a pressure reducing flow passage, which produces a back pressure substantially balancing the back pressure resulting from transmitting power through the working piston and the pressure intensifying pistons to produce a high pressure fluid flow through the output nozzle.
  • each shifting valve is made responsive not only tomovement of the piston to an end limit of travel proximate the-shifting valve, but is responsive also to pressurized working -fluid in its respective chamber being at a predetermined level.
  • Actuation of one or the other of the shifting valves causes a pressure imbalance at the control valve to cause rapid shifting of the control valve.
  • a centering spring urges the control valve toward its intermediate position.
  • the decrease in pressure causes deactivation of its related shifting valve to move the control valve to its intennediate position and stop further operation of the apparatus.
  • FIG. 1 is a semi-schematic side elevational view of the overall apparatus ,of the present invention
  • FIG. 2 is a viewpartly in sections of the pressure intensifying apparatus of the present invention
  • FIG. 3 is a sectional view of one of the shifting valves of the apparatus of FIG. 2;.
  • FIGS. 46 are semi-schematic drawings illustrating the operating'sequence of the present invention.
  • FIGS. 7A-7E are a series of semi-schematic'drawings showing the sequence of operation of the control valve of the present invention. 1
  • FIG. 8 is a graph illustrating the flow characteristics in the control valve in the sequence of operation of FIGS. 7A-7E; I
  • FIG. 9 is a graph illustrating the pressure characteristics-of the control valve in the sequence of operation of FIGS. 7A-7 E; I
  • FIG. 10 is a semi-schematic illustration of a second embodiment of the control valve of the present inventron
  • FIG. ;11 is a semi-schematic drawing of a third embodiment of the control valveof the present invention.
  • an electricmotor 10 which drives a hydraulic pump 14, which in turn supplies working fluid to a pressure intensifier unit 16.
  • the intensifier l6 draws fluid (i.e., water) from a suitable source, such as-a reservoir 18, and discharges the water at av'ery high pressure throughan'output, which as shown herein is a tube 20 with a small area exit nozzle 22. This results in a discharge of a fluid jet stream of a small diameter (e.g., 0.03 inches) and a very high velocity (e.g., 1,200 feet per second or greater).
  • the pressure intensifying unit 16 comprises a main housing 24, comprising a main cylinder 26, right and left end bell members 28 and 30, respectively, mounted to the ends of the cylinder 26, and right and left high pressure cylinders 32 and 34, respectively, threaded into respective bells 28 and 30.
  • a manifold block 36 Connected to the housing 24 is a manifold block 36 on which is mounted a flow'control valve 38.
  • a unitary piston assembly 40 Mounted for reciprocating motion within the housing 24 is a unitary piston assembly 40.
  • This assembly comprises a larger diameter central working piston 42 mounted within the main cylinder 26, and right and left high pressure pistons 44 and 46, respectively, extending oppositely from the center working piston 42.
  • the working piston 42 divides the interior of the main cylinder 26 into right and left working chambers 48 and 50 respectively.
  • the high pressure piston 44 reciprocates in the right high pressure chamber 52 defined by the right cylinder 32, while the left high pressure piston 46 reciprocates in the left high pressure chamber 54 defined by the other cylinder 34.
  • the aforementioned control valve 38 comprises a valve housing'56 defining a transfer chamber 58, in which is slide mounted a valve spool 60.
  • a valve spool 60 In the housing 56 is a centrally located high pressure fluid inlet port 62, right and left transfer ports 64 and 66, respectively, on opposite sides of the inlet port 62, and right and left low pressure outlet ports 68 and 70, respectively, positioned outside of the two transfer ports 64 and 66.
  • the valve spool 60 comprises right and left lands or pistons 72 and 74, respectively, and right and left outermost end closure members 76 and 78, respectively.
  • outside the two closure members 76 and 78 are respective right and left centering springs 80 and 82, respectively, which urge the spool 60 to its center position in the housing 56; each of the springs 80 and 82 has a stop collar 83 engaging a stop shoulder 83a to prevent either spring 80 or 82 urging the valve spool 60 beyond its center position.
  • the center port 62 is connected to a high pressure line from the pump 14, while the ports 68 and 70 are connected to the low pressure return line of the pump 14.
  • the right transfer port 64 connects to the right working chamber 48
  • the left transfer port 66 connects to the left working chamber 50.
  • the groove or chamber 84a located between the two piston elements 72 and 74 is a high pressure fluid transfer chamber, and functions to direct high pressure fluid from the port 62 to either the right transfer port 64 or the left transfer port 66 when in, respectively, a right or left hand position.
  • the right piston 72 and the right closure piston 76 define a groove or chamber 84b which is a low pressure transfer chamber that functions to connect the transfer port 64 with the low pressure outlet port 68 when the spool 60 is in its left hand position.
  • the left transfer piston 74 and left closure piston 78 define therebetween a groove or chamber 84c which functions to connect the left transfer port 66 with the low pressure outlet port when the spool 60 is in its right hand position.
  • each of the valves 85 and 86 comprises a sleeve 88 in which is slidably mounted a plug 90.
  • the plug is urged to its closed position by a compression spring 96.
  • an actuating pin 98 which butts against the plug 90 and extends through the housing to project into the end of its respective working chamber 48 or 50.
  • a locating stop 100 on the pin 98 properly positions the plug 90 in its closing position with the pin 98 extending into the chamber 48 or 50.
  • Through holes 101 in the plug 90 permit flow from the inlet port 92 to the venting port 94 when the plug 90 is pushed by pin 98 against the urging of the spring 96 to its open position shown in FIG. 3.
  • the inlet port 92 of the right shifting valve 85 is connected through an end opening 102 in the housing 56 of the valve 38 to a right control chamber 104 at the right end of the spool 60 of the valve 38, while the inlet port 92 of the left shifting valve 86 is similarly connected to the left control chamber 105 through opening 103 in the left of the valve 38.
  • valve 38 In describing the operations of this apparatus, for convenience the overall operation will first be described and then the means for starting the pumping action.
  • the valve 38 In FIG. 4, the valve 38 is in its left hand position,
  • the pumping pressure of the pump 14 is sufficiently large, relative to the force of the return springs 96 and the cross sectional area of the actuating pins 98 of the shifting valves 85 and 86, that when one of the working chambers 48 or 50 is pressurized by the pump 14, the resulting pressure on its related actuating pin 98 is suff cient to force the pin 98 against the urging of its related spring 96 to open the valve 85 or 86.
  • a portion of the high pressure working fluid is directed from the pump 14 to the valve control chambers 104 and 105 through respective restricted flow orifices 110 and 112, and also to the high pressure inlet ports 92 of the shifting valves 85 and 86.
  • each shifting valve 85 or 86 is connected to the pump reservoir 107.
  • its related valve control chamber .104 or 105 respectively, is pressurized, but when one of the valves 85 or 86 is open, its respective valve control chamber 104 or 105 is depressurized.
  • a starting valve this being shown schematically at 120.
  • the valve 120 has an up position where the right valve control chamber 104 is directly connected to the reservoir 107, a down position where the left valve control chamber 105 is connected to the reservoir 107, and an intermediate position where the valve 120 provides no operative connection to the chambers 104 and 105.
  • the starting valve 120 is shown in its center position where it has no effecton the operation of the apparatus.
  • the pump 14 has been turned off and theentire system has become depressurized, with the spool element of the valve 38 returning to its center position by action of the center-ing springs and 82. Further, let it be assumed that the working piston 42 is in some intermediate position, as shown in FIG; 4.
  • the pumping action will not startjBy pushing the valve to its down position
  • the left control chamber 105 becomes exposed to the low pressure pump reservoir 107 so that the high pressure in the right valve control chamber 104 causes the valve element 60 to move to the left (i.e., the position shown in FIG. 4.) to cause the piston 42 to move to the right.
  • the working piston 42 reaches its full right position to. engage the right actuating pin 98
  • the normal shifting sequence goes into effect as described above herein.
  • FIGS. 7A through 7E To describe in more detail the operation of the control valve 38, reference is now'made to FIGS. 7A through 7E.
  • the spool element 60 is shown in its full left position (shown schematically in FIG. 4), where the right piston 72 is positioned between the'high pressure port 62 and the right transfer port 64 so as to block any flow therebetween, while the left piston 74 is positioned so as to block any flow from the left transfer port 66 into the low pressure outlet port 70.
  • the right transfer port 64 communicates with the low pressure port 68 through the right low transfer chamber 84b sovthat the right working chamber 48 is depressurized.
  • thespool element 60 remains in this position until working piston 42 reaches its extreme right end of travel to cause shifting of the valve spool element 60 to the right.
  • valve element 60 is shown moving from its extreme left hand position through a position where it is just about to enter its intermediate position.
  • the laterally outermost portion 122 of the circumferential surfaces of each of the pistons 72 and 74 is substantially cylindrical so that it fits against the inner cylindrical surface of the housing 56.
  • the laterally inward circumferential surface portion 124 of each of the pistons 72 and 74 are tapered very moderately inwardly toward the middle of the spool element 60.
  • this taper is shown to be at a somewhat larger angle than normally used, this taper ordinarily being in the order of one degree from the longitudinal axis of the spool element 60. It can be seen that in the position shown in FIG. 7B the tapered surface 124 of the left piston 74 forms with the inner edge 126 of the left transfer port 66 a restricted circumferential flow passage 128.
  • a passage opens at 130 from the left transfer port 66 through the left low pressure transfer chamber 84c to the low pressure outlet port 70. Because of the very shallow taper of the surface 124, as soon as the spool element 60 moves a very short distance from the position of FIG. 7B, the passageway has a much larger cross sectional area than the passage of 128, so that there is a large pressure drop from the inlet port 62 across the passageway 128, and the pressure in the transfer port 66 almost immediately drops to the pump reservoir pressure that exists in the outlet port 70.
  • the spool 60 continues to move to the right from position 78 to that of 7C the left flow passage 128 becomes more restricted, while the right flow passage 128 defined by the piston 72 with the housing 56 becoming less restricted. Since the tapered surfaces 124 are both uniform, the rate of decrease of the cross section of the left restricted passage 128 is substantially the same as the rate of increase of the cross sectional area of the right restricted flow passage 128, so that the total flow rate through both passages 128 is constant. This is illustrated in the graph of FIG. 8, where the flow through the left restricted flow passage 128 is indicated at a and the right restricted flow passage 128 is indicated at b, with the combined-flow through both passages 128 being shown by the dotted line at c.
  • both the right and left transfer ports 64 and 66 are at the low pump reservoir pressure since the flow passages 130 have a substantially larger cross sectional flow area than the passages 128 (in the order of perhaps one hundred times as great when the spool element 60 is in the, position of FIG. 7C).
  • the total cross sectional area of the two restricted flow passages 128 remains substantially constant as the spool element 60 is moving through its intermediate phase from the position of FIG. 7B to that of 7D.
  • These two restricted flow passages 128 are, in effect, the same restricted flow pastially the same as the pressure existing-in either of the working chambers 48 and 50 when pressurized with the control Valve 38 in either'it's right or left position.
  • the effect of this is that when the valve element 60 is mov- 'ing from its right position through its intermediate position to its left position or vice versa, the back pressure exerted on the high pressure line from the pump 14 remains substantially constant, with the only pressure surges experienced being those caused by inertial forces of reversing the working piston 42.
  • the pressure balance is accomplished by properly selecting the effective total cross sectional area of the passages 128 relative to the effective cross sectional flow area of the output nozzle 22 and also relative to the effective pressure areas of the working piston 42 and the high pressure pistons 44 and 46, and to the frictional forces acting on the piston-assembly. To explain this relationship let us first assume these frictional forces are negligable and represent only a small correction to the relationship. It should be pointed out that the ratio of the pressure in either of the high pressure chambers 52 or 54 to the pressure in the working chamber 50 is'inversely proportional to the area of the piston 44 (which is the square of the radius of the piston 44 times 7r).
  • the pressure drop through the output nozzle 22 is proportional to the square of the average velocity of fluid flowfrom the nozzle 22 times the density of the output fluid (i.e., water).
  • the pressure drop across the flow passages "128 is proportional to the square of the average flow velocity of the fluid through the passages 128 times the density of the working fluid from the pump 14.
  • the effective cross sectional flow area of the passages 128, or of the passage shown schematically at 114 should be proportional to the effective cross sectional flow area of the nozzle 22 times the working area of the low pressure piston 42, divided by the pressure area of either of the pressure pistons 44or 46, multiplied by the square root of the ratio of the pressure area of the working piston 42 to the pressure area of the high pressure piston 44 and 46, multiplied by thev square root of the ratio of the density of the working fluid to the density of the output fluid.
  • thetotal effective cross sectional flow area of the restricted valve passageway (either the passages 128 or the schematic passage 114), should be eight times the effective cross sectional flow area of the nozzle 22.
  • the passages 128 would be chosen slightly smaller to correct for the additional pressure required for overcoming friction.
  • FIG.' 10 there is shown a second embodiment of the control valve of the present invention, in which components corresponding to thevalve 38 of the first embodiment will be given like numerical designations, with an a suffix distinguishing those of the second embodiment.
  • a housing 56a in which is mounted a valve spool 60a, comprising right and left pistons'72a and 74a, respectively, and right and left outermost end closure members 76a and 78a.
  • a valve spool 60a comprising right and left pistons'72a and 74a, respectively, and right and left outermost end closure members 76a and 78a.
  • these surface portions of the piston element 72a and 74a are stepped radially inwardly as at 124a.
  • valve element 60a passes through its intermediate position (corresponding to the movement of the valve element of the first embodiment as it moves from the position of FIGS. 7B to the position of FIG. 7D), there are two restricted flow passages 128a, through which there are substantially equal flows.
  • the combined effective cross sectional flow area of the two passages of 128a is such as toapproximate the back pressure exerted from the output nozzle back through the system to the pressurized working fluid.
  • FIG. 11 A third embodiment of the control valve of the present invention is illustrated in FIG. 11, In this valve, there is a housing in which there is a movable valve element 142 comprising a center piston 144 and two side pistons 146 and 147, respectively, and two end closure pistons 148 and 149, respectively. There is a center high pressure inlet port 150, right and left transfer ports 152 and 154, respectively, on opposite sides of the port 150, and right and left low pressure ports 156 and 158, respectively, located outside .the ports 152 and 154.
  • valve element 142 when the valve element 142 is in the right hand position, the right transfer port 152 communicates with the. low pressure port 156 to permit outflow of working fluid from its related working chamber, while high pressure fluid is being directed from the port through thetransfer port 154 to pressurize the other working chamber.
  • a hydraulic power apparatus for operation for example, as a pressure intensifying system to deliver a high pressure flow of output fluid, said apparatus comprising:
  • a working piston mounted in said working cylinder and separating said working cylinder into first and second working chambers, said working piston and cylinder being so arranged with inlet and outlet passage means as to receive pressurized working fluid of at least a predetermined pressure level alternately into said first and second working chambers, to cause said piston to reciprocate between opposite first and second end positions in said cylinder,
  • a control valve means to direct pressurized fluid from a working fluid source alternately to said first and second working chambers to cause the reciprocation of said working piston, said control valve means having first and second positions to direct pressurized fluid alternately to respectively said first and second working chambers,
  • a first shifting valve means operatively connected to said control valve means and having an actuating position where it causes said control valve means to be positioned in its first position to deliver pressurized working fluid to said first working chamber, said first shifting valve having first actuating means to move said first shifting valve means to its actuating position, which first actuating means is responsive to the piston moving to one of its end positions of travel and also responsive to working fluid mom of said chambers being at said predetermined pressure level, and
  • a second shifting valve means operatively connected to saidcontrol valve means and having an actuating position where it causes said control valve means to be positioned in its second position to deliver pressurized working fluid to said second working chamber, said second shifting valve means having second actuating means to move said second shifting valve means to its actuating position, which second actuating means is responsive to said piston'moving to the other of its end positions of travel and also responsive to working fluid in the other of said chambers being at said predetermined level.
  • each shifting valve means is positioned to be moved to its acutating position by engagement of said piston at its respective end position of travel, and also moved to its actuating position by exposure to pressure at said predtermined level in its respective working chamber.
  • control valve means has first and second control chambers, which, when pressurized and depressurized, move said control valve means between its first and second positions, said first shifting valve means being operatively connected to the first control chamber so as to reduce pressure in said first control chamber to move the control valve means to its first position, and said second shifting valve means being operatively connected to the second control chamber so as to reduce pressure in said second control chamber to move the control valve means to its second position.
  • said other positioning means comprises spring means which resiliently urges said control valve means to its intermediate position.
  • control valve means at its intermediate position functions to connect both said first and second working chambers to a low pressure area.
  • a hydraulic power apparatus for operation for example, as a pressure intensifying system, to deliver a high pressure stream of output fluid, said apparatus comprising:
  • a working piston mounted in said working cylinder and separating said working cylinder into first and second working chambers, said working piston and cylinder being so arranged as to receive pressurized working fluid of at least a predetermined pressure level alternately into said first and second working chambers, to cause said piston to reciprocate between opposite first and second end positions in said cylinder,
  • a control valve means to direct pressurized working fluid from a working fluid source alternately to said first and second working chambers to cause the reciprocation of said working piston
  • control valve means having-a first position where it delivers pressurized working fluid to said first chamber, a second position where it delivers pressurized working fluid to said second chamber, and a third intermediate position where said first and second working chambers are connected'to a lower pressure area,
  • control valve means having first and second control chambers, which, when pressurized and depressurized, moves said control valve means between its first and second positions,
  • control valve means having other valve positioning means arranged to urge said control valve means to its intermediate position
  • a first and second valve shifting means operatively connected to the control chambers of the control valve means in a manner to cause movement of the control valve means between its first and second positions, the first valve shifting means having an actuating position in which it is located-by said piston moving to one of its end positions of traveland also by action of said pressurized working fluidat said predetermined level in one of said chambers against said shifting valve means, said second shifting valve means also having an actuating position at which it is located by action of the piston moving to the other of its end positions of travel and also by pressurized working fluid at said predetermined level in the other of said working chambers acting against said second shifting valve means.
  • each of said'shifting valve means comprises an actuating memberwhich is positioned to be moved to its actuating position'by engagement with said piston at its related end position of travel-and. also positioned to. be exposed to pressure in its related working chamber to be moved to its actuating position.
  • said other positioning means comprises spring means which resilientlyurges said control valve means to its intermediate position.
  • valve operating means having a first position wherein said first control chamber is exposed to low pressure, and a second position wherein said sec- .ond control chamber is exposed to low pressure
  • control valve means can be moved between its first and second positions by operation of said other shifting valve means.
  • a hydragljgpgwer apparatus for operation as a pressure intensifying system to' delivr a high isatr flow of output fluid said apparatus comprising:
  • a working piston mounted in said working cylinder and separating said working cylinder into first and second working chambers, said working piston and cylinder being so arranged with inlet and outlet passage means as to receive pressurized working fluid of at least a predetermined pressure level alternately into said first and second workingchambers, to cause said piston to reciprocate between opposite first and second end positions in said cylinder, r
  • first and second high pressure output piston means operatively connected to said working piston so as to be moved along reciprocating paths thereby to deliver a high pressure flow of output fluid
  • a control valve means to direct pressurized working fluid from a working 'fluid source alternately 'to said first and second working chambers to cause the reciprocation of said working piston, I 1. said control valve means having a first position where it delivers pressurized working fluid to said second chamber to cause said working piston to move to its first end position, a second position where it delivers pressurized fluid to said first working chamber to cause said working piston to move to its second end position, and a third intermediate position where said first and second working chambers are connected to a lower pressure area,
  • control valve having first and second control chambers, which, when pressurized and depressurized, moves said control valve means between its first and second positions,
  • control valve means having other valve positioning means arranged to urge said control valve means to its intermediate position
  • a second valve shifting means having an actuating position and operatively connected to said second control chamber so as to depressurize said second control chamber when in its actuating position so as to initiate movement of said control valve means from its second position toward its first position,
  • said second valve shiftirigmeans being responsive its non-actuating position, and causes continued movement of said control valve means to its opposite position, thereby effecting rapid response of said control valve means betweenits first and second positions.
  • control valve means comprises spring means to urge said control valve means to its intermediate position.
  • each or said shifting valve meaiis comprisafiactuating member extending into a related working chamber, whereby each of said actuating members is responsive to pressure in its related chamber as well as to engagement of said working piston.
  • a first valve shifting means having an actuating po-

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US00322956A 1973-01-12 1973-01-12 High pressure fluid intensifier and method Expired - Lifetime US3811795A (en)

Priority Applications (14)

Application Number Priority Date Filing Date Title
US00322956A US3811795A (en) 1973-01-12 1973-01-12 High pressure fluid intensifier and method
CA189,213A CA1006787A (en) 1973-01-12 1973-12-31 High pressure fluid intensifier and method
GB44374A GB1420424A (en) 1973-01-12 1974-01-04 High pressure fluid intensifier and method
AU64259/74A AU483161B2 (en) 1974-01-07 High pressure fluid intensifier and method
ZA740112A ZA74112B (en) 1973-01-12 1974-01-07 High pressure fluid intensifier and method
IL43965A IL43965A (en) 1973-01-12 1974-01-07 Fluid pressure intensifier and method of alleviating potential pressure surges
IN74/CAL/74A IN141336B (enrdf_load_stackoverflow) 1973-01-12 1974-01-10
SE7400308A SE398911B (sv) 1973-01-12 1974-01-10 Tryckfluidumdriven kolvpump
DE2401341A DE2401341C2 (de) 1973-01-12 1974-01-11 Fluiddruck-Verstärkervorrichtung zur Erzeugung eines Hochdruck-Fluidstrahls
IT47665/74A IT1008123B (it) 1973-01-12 1974-01-11 Intensificatore di fluido ad alta pressione e metodo per alleviare po tenziali aumenti transitori di pres sione
NL7400433A NL7400433A (enrdf_load_stackoverflow) 1973-01-12 1974-01-11
FR7400963A FR2214051B1 (enrdf_load_stackoverflow) 1973-01-12 1974-01-11
JP49006937A JPS614997B2 (enrdf_load_stackoverflow) 1973-01-12 1974-01-12
ZM7/74A ZM774A1 (en) 1973-01-12 1974-01-14 High pressure fluid intensifier and method

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US00322956A US3811795A (en) 1973-01-12 1973-01-12 High pressure fluid intensifier and method

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US42744973A Continuation-In-Part 1973-01-12 1973-12-26

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US3811795A true US3811795A (en) 1974-05-21

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US00322956A Expired - Lifetime US3811795A (en) 1973-01-12 1973-01-12 High pressure fluid intensifier and method

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US (1) US3811795A (enrdf_load_stackoverflow)
FR (1) FR2214051B1 (enrdf_load_stackoverflow)
ZA (1) ZA74112B (enrdf_load_stackoverflow)
ZM (1) ZM774A1 (enrdf_load_stackoverflow)

Cited By (40)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3943823A (en) * 1974-06-13 1976-03-16 Nordson Corporation Control system for double acting air motor
DE2544129A1 (de) * 1974-10-02 1976-04-08 Flow Research Inc Schneidvorrichtung und -verfahren mit verwendung eines fluessigkeitsstrahls
US4378784A (en) * 1980-02-20 1983-04-05 Grumman Aerospace Corporation Solar heating system
US4381180A (en) * 1981-07-13 1983-04-26 Sell John R Double diaphragm pump with controlling slide valve and adjustable stroke
US4406596A (en) * 1981-03-28 1983-09-27 Dirk Budde Compressed air driven double diaphragm pump
US4494574A (en) * 1983-12-23 1985-01-22 International Telephone And Telegraph Corporation Valve arrangement for an air-operated diaphragm pump
US4526000A (en) * 1983-10-18 1985-07-02 Mccartney Manufacturing Co., Inc. Pressure intensifier
EP0223111A1 (en) * 1985-10-29 1987-05-27 DNA PLANT TECHNOLOGY CORPORATION (under the laws of the state of Delaware) An improved method for slicing fruits and vegetables
US4753549A (en) * 1986-08-29 1988-06-28 Nlb Corporation Method and apparatus for removing structural concrete
US4793734A (en) * 1987-10-22 1988-12-27 Nlb Apparatus for removing structural concrete
US4862911A (en) * 1988-11-14 1989-09-05 Fluidyne Corporation Check valve assembly for high pressure pumps
US5092744A (en) * 1990-03-14 1992-03-03 Possis Corporation Intensifier
US5337561A (en) * 1992-11-17 1994-08-16 Flow International Corporation Ultra high pressure multiple intensifier system
EP0636345A1 (en) * 1993-07-26 1995-02-01 Sentinel Medical, Inc. Fluid jet surgical cutting tool
US5520520A (en) * 1995-03-28 1996-05-28 Nakamoto; Tomijiko Pneumatically operated double acting pump for viscous food stuffs
WO1996018036A1 (en) * 1994-12-08 1996-06-13 HYTECH PUMPS INTERNATIONAL, INC. doing business as JETECH, INC. Pump pressure multiplier
US5527330A (en) * 1994-08-18 1996-06-18 United States Surgical Corporation Fluid cutting instrument
US5591184A (en) * 1994-10-13 1997-01-07 Sentinel Medical, Inc. Fluid jet surgical cutting instrument
US5735815A (en) * 1993-07-26 1998-04-07 Sentinel Medical, Inc. Method of using fluid jet surgical cutting tool
DE19652298A1 (de) * 1996-12-16 1998-06-18 Rexroth Mannesmann Gmbh Hochdruckpumpenanordnung
US5862828A (en) * 1996-07-10 1999-01-26 Hygrama Ag Oscillating valve for a double acting operating cylinder
WO1999014015A1 (en) * 1997-09-16 1999-03-25 Donald Stuart Miller Fluid abrasive jets for machining
NL1007912C2 (nl) * 1997-12-24 1999-06-25 Potma Beheer B V T Verliesarme flow regeling voor hydromotoren en cilinders werkend vanuit een accumulator zoals bij toepassing van een vrije-zuiger aggregaat.
WO1999034100A1 (en) * 1997-12-24 1999-07-08 T. Potma Beheer B.V. Device for digital hydraulic pressure transformation (dhpt)
US6769695B2 (en) 2001-12-14 2004-08-03 Kmt Waterjet Systems, Inc. Back-up rings for high pressure seals, packing assembly, and pumps incorporating same
US20060144222A1 (en) * 2004-12-30 2006-07-06 Dan Paval Pneumatic reciprocating motor
US20070286746A1 (en) * 2006-06-08 2007-12-13 Thrasher William B Ventless gas-driven pumping system
US20110176940A1 (en) * 2008-07-08 2011-07-21 Ellis Shawn D High pressure intensifier system
US20140199182A1 (en) * 2013-01-11 2014-07-17 Super Products Llc Reciprocating water pump
CN105889153A (zh) * 2014-10-09 2016-08-24 中国科学院地质与地球物理研究所 双向作动气驱伺服液压增压装置
US20170184090A1 (en) * 2013-01-11 2017-06-29 Super Products Llc Reciprocating water pump
US9926947B2 (en) * 2014-05-09 2018-03-27 Montana Hydraulics, LLC Air-to-hydraulic fluid pressure amplifier
US10138877B2 (en) * 2016-11-11 2018-11-27 Vector Technologies Llc Method and system for intensifying slurry pressure
US10160134B2 (en) 2016-03-01 2018-12-25 Key Technology, Inc. Method of cutting and cutting apparatus using high pressure liquid
US11041510B2 (en) * 2017-10-19 2021-06-22 Pistonpower Aps Hydraulic pressure amplifier arrangement
WO2021138679A1 (en) * 2020-01-03 2021-07-08 The Oil Gear Company Subsea hydraulic pressure boosting and regulating system
US20240052818A1 (en) * 2019-09-19 2024-02-15 Oshkosh Corporation Reciprocating piston pump
US20240159255A1 (en) * 2021-03-31 2024-05-16 Eagle Industry Co., Ltd. Fluid circuit
US12292060B2 (en) 2021-03-31 2025-05-06 Eagle Industry Co., Ltd. Fluid circuit
US12404847B2 (en) * 2023-10-23 2025-09-02 Oshkosh Corporation Reciprocating piston pump

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CN104912855B (zh) * 2015-06-11 2017-03-01 哈尔滨工程大学 一种可应用于深海环境的自动换向海水增压器
FR3083271B1 (fr) * 2018-06-27 2020-09-04 Safran Landing Systems Procede de commande d'un distributeur a tiroir a trois positions

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US3465686A (en) * 1967-10-16 1969-09-09 Francis A Nugier Air operated hydraulic pump
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US3540348A (en) * 1965-05-20 1970-11-17 Hermann Joseph Pennther Fluid operated continuously actuated reciprocating piston drive
US3465686A (en) * 1967-10-16 1969-09-09 Francis A Nugier Air operated hydraulic pump

Cited By (52)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3943823A (en) * 1974-06-13 1976-03-16 Nordson Corporation Control system for double acting air motor
DE2544129A1 (de) * 1974-10-02 1976-04-08 Flow Research Inc Schneidvorrichtung und -verfahren mit verwendung eines fluessigkeitsstrahls
US4378784A (en) * 1980-02-20 1983-04-05 Grumman Aerospace Corporation Solar heating system
US4406596A (en) * 1981-03-28 1983-09-27 Dirk Budde Compressed air driven double diaphragm pump
US4381180A (en) * 1981-07-13 1983-04-26 Sell John R Double diaphragm pump with controlling slide valve and adjustable stroke
US4526000A (en) * 1983-10-18 1985-07-02 Mccartney Manufacturing Co., Inc. Pressure intensifier
US4494574A (en) * 1983-12-23 1985-01-22 International Telephone And Telegraph Corporation Valve arrangement for an air-operated diaphragm pump
EP0223111A1 (en) * 1985-10-29 1987-05-27 DNA PLANT TECHNOLOGY CORPORATION (under the laws of the state of Delaware) An improved method for slicing fruits and vegetables
US4751094A (en) * 1985-10-29 1988-06-14 Dna Plant Technology Corp. Method for slicing fruits and vegetables
US4753549A (en) * 1986-08-29 1988-06-28 Nlb Corporation Method and apparatus for removing structural concrete
US4793734A (en) * 1987-10-22 1988-12-27 Nlb Apparatus for removing structural concrete
US4862911A (en) * 1988-11-14 1989-09-05 Fluidyne Corporation Check valve assembly for high pressure pumps
US5092744A (en) * 1990-03-14 1992-03-03 Possis Corporation Intensifier
US5337561A (en) * 1992-11-17 1994-08-16 Flow International Corporation Ultra high pressure multiple intensifier system
EP0636345A1 (en) * 1993-07-26 1995-02-01 Sentinel Medical, Inc. Fluid jet surgical cutting tool
US5853384A (en) * 1993-07-26 1998-12-29 Surgijet, Inc. Fluid jet surgical cutting tool and aspiration device
US5735815A (en) * 1993-07-26 1998-04-07 Sentinel Medical, Inc. Method of using fluid jet surgical cutting tool
US5562692A (en) * 1993-07-26 1996-10-08 Sentinel Medical, Inc. Fluid jet surgical cutting tool
US5527330A (en) * 1994-08-18 1996-06-18 United States Surgical Corporation Fluid cutting instrument
US5591184A (en) * 1994-10-13 1997-01-07 Sentinel Medical, Inc. Fluid jet surgical cutting instrument
US5588808A (en) * 1994-12-08 1996-12-31 Hytech Pumps International, Inc. Pump pressure multiplier
WO1996018036A1 (en) * 1994-12-08 1996-06-13 HYTECH PUMPS INTERNATIONAL, INC. doing business as JETECH, INC. Pump pressure multiplier
US5520520A (en) * 1995-03-28 1996-05-28 Nakamoto; Tomijiko Pneumatically operated double acting pump for viscous food stuffs
US5862828A (en) * 1996-07-10 1999-01-26 Hygrama Ag Oscillating valve for a double acting operating cylinder
DE19652298A1 (de) * 1996-12-16 1998-06-18 Rexroth Mannesmann Gmbh Hochdruckpumpenanordnung
WO1999014015A1 (en) * 1997-09-16 1999-03-25 Donald Stuart Miller Fluid abrasive jets for machining
US6276993B1 (en) 1997-09-16 2001-08-21 Donald Stuart Miller Fluid abrasive jets for machining
NL1007912C2 (nl) * 1997-12-24 1999-06-25 Potma Beheer B V T Verliesarme flow regeling voor hydromotoren en cilinders werkend vanuit een accumulator zoals bij toepassing van een vrije-zuiger aggregaat.
WO1999034100A1 (en) * 1997-12-24 1999-07-08 T. Potma Beheer B.V. Device for digital hydraulic pressure transformation (dhpt)
US6564547B1 (en) 1997-12-24 2003-05-20 T. Potma Beheer, B.V. Device for digital hydraulic pressure transformation (DHPT)
US6769695B2 (en) 2001-12-14 2004-08-03 Kmt Waterjet Systems, Inc. Back-up rings for high pressure seals, packing assembly, and pumps incorporating same
US20060144222A1 (en) * 2004-12-30 2006-07-06 Dan Paval Pneumatic reciprocating motor
US7284475B2 (en) * 2004-12-30 2007-10-23 Envirodrive Inc. Pneumatic reciprocating motor
US20070286746A1 (en) * 2006-06-08 2007-12-13 Thrasher William B Ventless gas-driven pumping system
US20110176940A1 (en) * 2008-07-08 2011-07-21 Ellis Shawn D High pressure intensifier system
US20140199182A1 (en) * 2013-01-11 2014-07-17 Super Products Llc Reciprocating water pump
US20170184090A1 (en) * 2013-01-11 2017-06-29 Super Products Llc Reciprocating water pump
US9926947B2 (en) * 2014-05-09 2018-03-27 Montana Hydraulics, LLC Air-to-hydraulic fluid pressure amplifier
CN105889153A (zh) * 2014-10-09 2016-08-24 中国科学院地质与地球物理研究所 双向作动气驱伺服液压增压装置
US10160134B2 (en) 2016-03-01 2018-12-25 Key Technology, Inc. Method of cutting and cutting apparatus using high pressure liquid
US10500753B2 (en) 2016-03-01 2019-12-10 Key Technology, Inc. Method of cutting and cutting apparatus using high pressure liquid
US10138877B2 (en) * 2016-11-11 2018-11-27 Vector Technologies Llc Method and system for intensifying slurry pressure
US11041510B2 (en) * 2017-10-19 2021-06-22 Pistonpower Aps Hydraulic pressure amplifier arrangement
US20240052818A1 (en) * 2019-09-19 2024-02-15 Oshkosh Corporation Reciprocating piston pump
WO2021138679A1 (en) * 2020-01-03 2021-07-08 The Oil Gear Company Subsea hydraulic pressure boosting and regulating system
US11401954B2 (en) * 2020-01-03 2022-08-02 The Oilgear Company Subsea hydraulic pressure boosting and regulating system
US20230058722A1 (en) * 2020-01-03 2023-02-23 The Oilgear Company Subsea hydraulic pressure boosting and regulating system
US12258980B2 (en) * 2020-01-03 2025-03-25 The Oilgear Company Subsea hydraulic pressure boosting and regulating system
US20240159255A1 (en) * 2021-03-31 2024-05-16 Eagle Industry Co., Ltd. Fluid circuit
US12281663B2 (en) * 2021-03-31 2025-04-22 Eagle Industry Co., Ltd. Fluid circuit
US12292060B2 (en) 2021-03-31 2025-05-06 Eagle Industry Co., Ltd. Fluid circuit
US12404847B2 (en) * 2023-10-23 2025-09-02 Oshkosh Corporation Reciprocating piston pump

Also Published As

Publication number Publication date
FR2214051B1 (enrdf_load_stackoverflow) 1978-01-06
ZA74112B (en) 1974-12-24
ZM774A1 (en) 1974-10-21
FR2214051A1 (enrdf_load_stackoverflow) 1974-08-09

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