US2866415A - Hydraulic transformers - Google Patents

Hydraulic transformers Download PDF

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Publication number
US2866415A
US2866415A US443903A US44390354A US2866415A US 2866415 A US2866415 A US 2866415A US 443903 A US443903 A US 443903A US 44390354 A US44390354 A US 44390354A US 2866415 A US2866415 A US 2866415A
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piston
liquid
pressure
pistons
valve
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US443903A
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Bratt John
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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
    • F04B9/109—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 having plural pumping chambers
    • F04B9/117—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 having plural pumping chambers the pumping members not being mechanically connected to each other
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L25/00—Drive, or adjustment during the operation, or distribution or expansion valves by non-mechanical means
    • F01L25/02—Drive, or adjustment during the operation, or distribution or expansion valves by non-mechanical means by fluid means
    • F01L25/04—Drive, or adjustment during the operation, or distribution or expansion valves by non-mechanical means by fluid means by working-fluid of machine or engine, e.g. free-piston machine
    • F01L25/06—Arrangements with main and auxiliary valves, at least one of them being fluid-driven
    • F01L25/063—Arrangements with main and auxiliary valves, at least one of them being fluid-driven the auxiliary valve being actuated by the working motor-piston or piston-rod
    • 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
    • F04B19/00—Machines or pumps having pertinent characteristics not provided for in, or of interest apart from, groups F04B1/00 - F04B17/00
    • F04B19/02—Machines or pumps having pertinent characteristics not provided for in, or of interest apart from, groups F04B1/00 - F04B17/00 having movable cylinders
    • F04B19/022—Machines or pumps having pertinent characteristics not provided for in, or of interest apart from, groups F04B1/00 - F04B17/00 having movable cylinders reciprocating cylinders
    • 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
    • F04B9/109—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 having plural pumping chambers
    • F04B9/117—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 having plural pumping chambers the pumping members not being mechanically connected to each other
    • F04B9/1176—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 having plural pumping chambers the pumping members not being mechanically connected to each other the movement of each piston in one direction being obtained by a single-acting piston liquid motor
    • 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

  • the present invention relates to hydraulic transformers for continuously transforming a supplied stream of liquid to another stream of liquid having a higher or lower pressure and a correspondingly lower or higher rate of flow respectively, and relates more particularly to a hydraulic transformer of the type comprising at least two pistons, each operating in a cylinder and to one side of which in order to effect the working stroke a pressure liquid is supplied by means of one or more reversing valves and in which the return stroke of the pistons is efiected by pressure liquid supplied to the opposite side of the pistons.
  • the pressure liquid employed for the return stroke of the pistons is separate from the pressure liquid used for the working stroke, the latter pressure liquid being used solely to effect the working stroke, and the amount of pressure liquid used to return the pistons is so regulated in relation to the amount of pressure liquid used to effect the working stroke, that the total time of reversing the valves and returning a piston is less than the time of the working stroke of a piston, whereby in every working position of the device the discharge transformed liquid stream will be uniform with respect to rate of fiow as well as pressure.
  • the reversing valve or valves may be so arranged that before a piston reaches the end point of its working stroke a second piston is gradually put into operation with a simultaneous decrease of the rate of pressure liquid supplied to the first piston, in order that the hydraulic output vwill be maintained uniform.
  • the reversing valve is adapted to be reversed directly or through a limit valve by the intermediary of resilient abutments actuated by the pistons in one of their end positions.
  • the limit valve is also adapted to be manually actuated.
  • each movable piston has a concentric bore closed at one end and forming a cylinder for a stationary piston.
  • the working movable pistons have piston rods extending through gaskets in the cylinder end walls and each driving a piston pump with suction and pressure valves for pumping a second liquid.
  • Figure 1 is a longitudinal cross-section taken along line 1-1 in Figure 2.
  • Figures 2 is a transverse cross-section taken along line cross-section as Figure 1 with the moving parts in an-.
  • Figure 7 illustrates the second embodiment.
  • the numeral 21 represents a valve body affixed to the top wall 22 of a liquid tank.
  • Two casings 23, each closed at one end by an end-plate 24, are formed at their opposed ends with square flanges 25 which are screwed to opposed sides of the body 21, while simultaneously clamping therebetween the flanges 27 of a pair of cylinders 26 so that these cylinders Will be concentric With a stationary piston rod 23 extending through the body 21.
  • the piston rod 28 has packing rings 29 at its outer ends.
  • Two movable pistons 30 and 3i, each having a central bore 32 extending part way theret'nrough are adapted to slide on and to engage sealingly the inner surfaces of the cylinders 26 as well as the packing rings 29.
  • Two bores 33 provided in the body 21 and extending above the stationary piston rod 28 are shown in Figures 2 and 3. These bores 33 are closed at opposite ends by threaded plugs 34 and receive sleeves which contain four non-return valves 35 and 36, which allow liquid to pass from the chambers 37 to the chambers 38 and from the chambers 38 to the chambers 39, but not in the opposite direction.
  • a pressure liquid inlet passage 40 communicates through lateral passages in the sleeve walls with the two chambers 37, while a pressure liquid outlet passage 41 communicates in a similar manner with the two chambers 39.
  • Each of the two intermediate chambers 38 communicates through transverse bores 42 in the housing 21 and longitudinal bores 43 in the stationary piston rod 28 with one of the working chambers 44 within the pistons 3t) and 31, as seen in Figure 1.
  • 45 is a piston limit valve and 55 a reversing valve which are shown in different positions in Figures 1 and 5 in cross-section taken along line 1--1 in Figure 2.
  • the piston 45 of the limit valve may be displaced a short distance between two abutment rings -47 at the ends of a bore 46 provided in the housing 21 and open at both ends.
  • the intermediate space of the piston valve 45 is maintained under pressure through the pressure conduit 40 and when the valve piston is displaced towards one or the other side, one of the two grooves 50 is set under liquid pressure, while the other groove 50 is brought into communication with the chamber 51 outside the valve body 21.
  • the two chambers 51 communicate through the transverse bore 52 and are kept at atmospheric pressure via an outlet 53 and an air intake 54, as seen in Fi ure 2.
  • the piston 56 of the reversing valve 55 is displaceable in its bore, which is closed at each end by a cover-plate 57.
  • Each of the two end chambers 58 between the piston 56 and the cover-plates 57 communicate with one of the grooves 50 through the inclined bores 59 ( Figures 1, 2 and 5).
  • the valve piston 45 When the valve piston 45 is moved from one side to the other, the pressure difference between the inlet 61 while the two outer grooves 62 have free discharge to a liquid reservoir through the outlets 63.
  • the two remaining grooves 64 are deeper than the other grooves and each of them communicates through a bore 65 with one of the chambers 20 between the outer casing 23, the outside of the cylinder 26 and the outer end of the piston 30 or 31.
  • the intermediate portion of the valve piston 55 is formed with a cylindrical part 66 hav' ing slightly tapered ends 67 so formed that when the valve piston 55 is displaced the pressure groove 60 is gradually connected with one of the grooves 64 and simultaneously the previously open communication from the pressure groove 60 to the other groove 64 is gradually closed.
  • a motor 68 drives a main pump 69 as well as an auxiliary pump 70.
  • the main pump 69 takes liquid from a reservoir 71 and delivers the liquid through the conduit 72 to the pressure liquid inlet 61 (see Figures 1,4 and from which the liquid in accordance with-the position of the valve piston 55 passes to one or .both of .the chambers 20.
  • the auxiliary pump 78 takes liquid from a liquid reservoir 74 and delivers it through the conduit 75 to the pressure inlet 40 ( Figures 1, 2, 3, 4 and 5).
  • the pressure in the conduit 75 is controlled by an overflow valve '76 having an outlet 77 to the reservoir 74.
  • the liquid stream delivered to the chamber 28 by the main pump 69 and having a relatively low pressure and a relatively high rate of flow will thereby be transformed into a liquid stream taken from auxiliary pump 70 and having a relatively low rate of flow, but a relatively high pressure.
  • the function is illustrated by the graphical representation in Figure 6, where the horizontal axis represents the time and the vertical axis the positions of pistons 30 and 31.
  • the numbers 1 to 8 refer to the various positions of piston 30.
  • the numbers 1, 2 and 8 correspond to the outer end position of the piston 38 as shown in Figure 1, while the numbers 6 and 7 correspond to the inner end position of piston 30.
  • the numbers 11 to 18 correspond to the positions of piston 31.
  • valve piston 45 In the positions of the valves and pistons which are shown in Figure 1, the valve piston 45 is in its right-hand end position.
  • the pressure in the pressure conduit 40 communicating with the auxiliary pump 70 is transmitted to the right-hand groove 50 and from this it enters through the bore 59 the right-hand end-chamber 58 of the piston valve 55, whereby the valve piston 56 will be brought into its left-hand end position.
  • the space 20 around the left-hand cylinder 26 which communicates through bore 65 with the left-hand groove 64 of the reversing valve 56 then communicates with the groove 62 and its outlet 63, wherefore it is pressure-free.
  • the chamber 44 within the piston 30, is under pressure in that that chamber communicates through one of the ncnreturn valves 35, one of the chambers 38 and the bores 42 and 43 with the pressure liquid supply conduit 48, so that the piston 30 is kept in its outer end position.
  • the other piston 31 receives pressure liquid from the main pump 69 through conduit 72, inlet 61, the passage from the groove 60 to the right-hand groove 64 and through the bore 65 to the chamber 20 at the outer end of the piston 31. Thereby, the piston 31 will be displaced inwardly, whereby the liquid in its chamber 44 will be forced through the bores 43 and 42 to the chamber 38 ( Figure 3) and from this through a non-return valve 36 to the chamber 39 and to the pressure liquid outlet conduit 41, as explained above.
  • Point 14 in Figure 6 refers to the position of piston 31 in which this engages the limit valve 45, as shown in Figure 1.
  • the valve 45 will be displaced to the left, whereby the pressure of the auxiliary pump 78 through the pressure conduit 40 and the corresponding bore 59 will act in the left-hand chamber 58 instead, whereby the valve piston 56 will be displaced to the right.
  • the chamber 28 of the piston 30 will be disconnected by the edge 78 of thepiston valve 55 .reaching the edge 79 the abutments 83 of piston 45 resilient.
  • said abutments are formed as small pistons, each of which is movable in a bushing 84 screwed into valve 45 and is subjected to fluid pressure in the chamber 85, which communicates through bores 86 with the pressure conduit 40 of the auxiliary pump.
  • a spring 87 can be employed instead of or together with the hydraulic resiliency.
  • valve body may be provided with a piston 88 which extends through a threaded plug 90 with a gasket 91 and can be turned through a certain angle by means of a handle 89.
  • An eccentric pin 92 secured to the piston 88 will then act upon the piston 45 and displace it towards either side.
  • the condition to be fulfilled in order that the device shall function in the desired manner is that the pistons 30 and 31 are always returned at the right moment, i. e. that (see Figure 6) the point 18, when the piston 31 is in its outer end position, occurs prior to point 4 when the piston 30 reverses valve 45 and that similarly, the point 8, when the piston 30 is in its outer end position occurs prior to point 14 when piston 31 reverses the valve 45.
  • the embodiment illustrated which has separate liquid reservoirs 71 and 74 is convenient in case the highpressure conduit 41 shall convey a poorly lubricating liquid, since then it is possible to have the main pump 69 operating with a more suitable liquid.
  • the embodiment of Figure 7 is suitable.
  • Both the main pump 69 and the auxiliary pump 70 in this embodiment take liquid, suitably lubricating oil, from the same reservoir 93 and the working pistons 30 and 31 have stout piston rods 94, each driving a single-acting piston 95 movable in a cylinder 96 having suction valves 103 and pressure valves 104, a suction inlet 97 and a pressure outlet 98 for the corrosive or impure liquid.
  • the pistons 35) and 31 with their pump cylinders are attached to a common bottom plate 101 having gaskets 102 for the piston rods 94.
  • the conduit arrangement of the main pump is entirely similar to that described in connection with Figure 4.
  • the auxiliary pump 70 delivers its pressure liquid directly without non-return valves to the chambers 44 below the pistons 30 and 31, while the discharge conduit 41 of Figures 2, 3, 4 with the nonreturn valves 36 is omitted.
  • the limit valve 45 is suitably formed as a rotary valve actuated by resilient arms 99, which are operated in the movement of the piston rods 94 by abutment flanges 100 secured thereto.
  • a hydraulic transformer for continuously transforming a supplied liquid stream into a liquid stream of difierent flow rate and pressure comprising two stationary cylinders, two pistons movable in said stationary cylinders and having cylinder forming bores, two stationary pistons each extending into one of said cylinder forming bores, means for alternatingly supplying a first pressure liquid to the other sides of each of said movable pistons to effect the piston working stroke, means for supplying a second pressure liquid to the cylinder forming bores in each of said movable pistons to effect the piston return stroke and to form upon the working stroke of its piston the transformed liquid stream, means for receiving the transformed liquid streams from both pistons, valve means restricting the transformed liquid flow to flow from said pistons to said receiving means, said second pressure liquid completing the return stroke of each piston before the other piston reaches the end of its working stroke, said first mentioned supplying means acting to supply the first pressure liquid to each piston before the other piston reaches the end of its working stroke
  • a hydraulic transformer as specified in claim 1 in which said stationary cylinders are in opposed longitudinal axial positions, said stationary pistons are in opposed 6 longitudinal axial positions and in which the supply of second pressure liquid is through said stationary pistons to the cylinder forming bores in said movable pistons.
  • a hydraulic transformer for continuously transforming a supplied liquid stream into a liquid stream of different flow rate and pressure comprising two cylinders, two movable pistons each operating in one of said cylinders, means actuated by said pistons for alternatingly supplying a first pressure liquid to one side of each of said pistons to effect the piston working stroke, means for supplying a second pressure liquid to the other sides of each of said pistons to effect the piston return stroke and forming upon the working stroke of its piston the transformed liquid stream, means for receiving the trans formed liquid streams from both pistons, valve means restricting the transformed liquid flow to flow from said pistons to said receiving means, said second pressure liquid completing the return stroke of each piston before the other piston reaches the end of its working stroke, said first mentioned supplying means acting to supply the first pressure liquid to each piston before the other piston reaches the end of its working stroke and including means for supplying pressure liquid to each of the pistons before interrupting the supply thereof to the other piston and means for gradually decreasing the rate of supply of said first pressure liquid to each piston while gradually increasing the rate of supply
  • a hydraulic transformer for continuously transforming a supplied liquid stream into a liquid stream of different flow rate and pressure comprising two cylinders, two movable pistons each operating in one of said cylinders, a fluid operated reversing valve for alternatingly supplying a first pressure liquid to one side of each of said pistons to effect the piston working stroke, valve means actuated by said pistons for controlling flow of operating fluid to said reversing valve, means for supplying a second pressure liquid to the other sides of each of said pistons to effect the piston return stroke and forming upon the working stroke of its piston the transformed liquid stream, means for receiving the transformed liquid streams from both pistons, valve means restricting the transformed liquid flow to flow from said pistons to said receiving means, said first pressure liquid being used solely to effect the piston working stroke, said second pressure liquid completing the return stroke of each piston before the other piston reaches the end of its working stroke, each piston actuating said second mentioned valve to actuate said reversing valve before the piston reaches the end of its working stroke, and said reversing valve
  • valve means actuated by the pistons for controlling flow of operating fluid to the reversing valve is actuated by said pistons through resilient abutments.
  • a hydraulic transformer as specified in claim 5 including means for manually actuating said second mentioned valve means.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Reciprocating Pumps (AREA)
US443903A 1953-07-15 1954-07-13 Hydraulic transformers Expired - Lifetime US2866415A (en)

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SE341716X 1953-07-15

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US (1) US2866415A (en(2012))
BE (1) BE530403A (en(2012))
CH (1) CH341716A (en(2012))
FR (1) FR1110783A (en(2012))
NL (2) NL88684C (en(2012))

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2977040A (en) * 1957-08-09 1961-03-28 Dayton Rogers Mfg Co Pneumatic pressure boosting apparatus
US3183840A (en) * 1962-08-03 1965-05-18 Lynes Inc Pump
US3205825A (en) * 1963-11-18 1965-09-14 Kojabashian Charles Proportioning pump
US3331329A (en) * 1964-08-25 1967-07-18 Burckhardt Ag Maschf Single acting twin cylinder pump or compressor
US3363575A (en) * 1966-01-24 1968-01-16 Cicero C Brown Fluid pressure-driven multiplex pump
US3425498A (en) * 1965-11-19 1969-02-04 Dowty Technical Dev Ltd Fluid actuated vibrator devices
US3440967A (en) * 1966-01-13 1969-04-29 Leffer Stahl & App Fluid pressure source with booster
US3791768A (en) * 1972-06-16 1974-02-12 W Wanner Fluid pump
US4496294A (en) * 1981-12-22 1985-01-29 Champion Spark Plug Company Diaphragm pump
US4543044A (en) * 1983-11-09 1985-09-24 E. I. Du Pont De Nemours And Company Constant-flow-rate dual-unit pump
DE8815312U1 (de) * 1988-12-09 1989-02-09 Hydac Technology GmbH, 6603 Sulzbach Druckübersetzer
US20080260551A1 (en) * 2007-01-26 2008-10-23 Walter Neal Simmons Rolling diaphragm pump

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3811795A (en) * 1973-01-12 1974-05-21 Flow Research Inc High pressure fluid intensifier and method

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US825950A (en) * 1905-09-28 1906-07-17 William Weir Steam-engine air-pump.
US2141731A (en) * 1935-05-11 1938-12-27 Ig Farbenindustrie Ag Double cylinder water pressure engine and piston pump actuated thereby
US2186968A (en) * 1938-07-18 1940-01-16 Byron Jackson Co Pumping apparatus
US2528131A (en) * 1947-11-28 1950-10-31 Phillips Petroleum Co Hydraulic pumping unit
US2579670A (en) * 1948-04-02 1951-12-25 Skf Svenska Kullagerfab Ab Hydraulic pressure transformer
US2660955A (en) * 1950-06-27 1953-12-01 Hydropress Inc Hydraulic machine

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US825950A (en) * 1905-09-28 1906-07-17 William Weir Steam-engine air-pump.
US2141731A (en) * 1935-05-11 1938-12-27 Ig Farbenindustrie Ag Double cylinder water pressure engine and piston pump actuated thereby
US2186968A (en) * 1938-07-18 1940-01-16 Byron Jackson Co Pumping apparatus
US2528131A (en) * 1947-11-28 1950-10-31 Phillips Petroleum Co Hydraulic pumping unit
US2579670A (en) * 1948-04-02 1951-12-25 Skf Svenska Kullagerfab Ab Hydraulic pressure transformer
US2660955A (en) * 1950-06-27 1953-12-01 Hydropress Inc Hydraulic machine

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2977040A (en) * 1957-08-09 1961-03-28 Dayton Rogers Mfg Co Pneumatic pressure boosting apparatus
US3183840A (en) * 1962-08-03 1965-05-18 Lynes Inc Pump
US3205825A (en) * 1963-11-18 1965-09-14 Kojabashian Charles Proportioning pump
US3331329A (en) * 1964-08-25 1967-07-18 Burckhardt Ag Maschf Single acting twin cylinder pump or compressor
US3425498A (en) * 1965-11-19 1969-02-04 Dowty Technical Dev Ltd Fluid actuated vibrator devices
US3440967A (en) * 1966-01-13 1969-04-29 Leffer Stahl & App Fluid pressure source with booster
US3363575A (en) * 1966-01-24 1968-01-16 Cicero C Brown Fluid pressure-driven multiplex pump
US3791768A (en) * 1972-06-16 1974-02-12 W Wanner Fluid pump
US4496294A (en) * 1981-12-22 1985-01-29 Champion Spark Plug Company Diaphragm pump
US4543044A (en) * 1983-11-09 1985-09-24 E. I. Du Pont De Nemours And Company Constant-flow-rate dual-unit pump
DE8815312U1 (de) * 1988-12-09 1989-02-09 Hydac Technology GmbH, 6603 Sulzbach Druckübersetzer
US20080260551A1 (en) * 2007-01-26 2008-10-23 Walter Neal Simmons Rolling diaphragm pump

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Publication number Publication date
FR1110783A (fr) 1956-02-16
NL189160B (nl)
CH341716A (de) 1959-10-15
NL88684C (en(2012))
BE530403A (en(2012))

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