EP2009283A2 - Verbesserung für eine hydraulisch angetriebene Maschine - Google Patents

Verbesserung für eine hydraulisch angetriebene Maschine Download PDF

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Publication number
EP2009283A2
EP2009283A2 EP20080163603 EP08163603A EP2009283A2 EP 2009283 A2 EP2009283 A2 EP 2009283A2 EP 20080163603 EP20080163603 EP 20080163603 EP 08163603 A EP08163603 A EP 08163603A EP 2009283 A2 EP2009283 A2 EP 2009283A2
Authority
EP
European Patent Office
Prior art keywords
machine
cylinder
bellows
cam
fluid
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP20080163603
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English (en)
French (fr)
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EP2009283B1 (de
EP2009283A3 (de
Inventor
Jan Eysymontt
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Garniman SA
Original Assignee
Garniman SA
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Garniman SA filed Critical Garniman SA
Priority to EP08163603.7A priority Critical patent/EP2009283B1/de
Publication of EP2009283A2 publication Critical patent/EP2009283A2/de
Publication of EP2009283A3 publication Critical patent/EP2009283A3/de
Application granted granted Critical
Publication of EP2009283B1 publication Critical patent/EP2009283B1/de
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • 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
    • F04B9/103—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 only one pumping chamber
    • F04B9/105—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 only one pumping chamber reciprocating movement of the pumping member being obtained by a double-acting liquid motor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B19/00—Positive-displacement machines or engines of flexible-wall type
    • F01B19/04—Positive-displacement machines or engines of flexible-wall type with tubular flexible members
    • 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
    • F01L21/00—Use of working pistons or pistons-rods as fluid-distributing valves or as valve-supporting elements, e.g. in free-piston machines
    • F01L21/04—Valves arranged in or on 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
    • F04B43/00—Machines, pumps, or pumping installations having flexible working members
    • F04B43/08—Machines, pumps, or pumping installations having flexible working members having tubular flexible members
    • F04B43/10—Pumps having fluid drive
    • F04B43/113—Pumps having fluid drive the actuating fluid being controlled by at least one valve
    • 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
    • F04B43/00—Machines, pumps, or pumping installations having flexible working members
    • F04B43/08—Machines, pumps, or pumping installations having flexible working members having tubular flexible members
    • F04B43/10—Pumps having fluid drive
    • F04B43/113—Pumps having fluid drive the actuating fluid being controlled by at least one valve
    • F04B43/1133—Pumps having fluid drive the actuating fluid being controlled by at least one valve with fluid-actuated pump inlet or outlet valves; with two or more pumping chambers in series
    • 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
    • F04B43/00—Machines, pumps, or pumping installations having flexible working members
    • F04B43/08—Machines, pumps, or pumping installations having flexible working members having tubular flexible members
    • F04B43/10—Pumps having fluid drive
    • F04B43/113—Pumps having fluid drive the actuating fluid being controlled by at least one valve
    • F04B43/1136—Pumps having fluid drive the actuating fluid being controlled by at least one valve with two or more pumping chambers in parallel

Definitions

  • the invention relates to hydraulically driven machines, in particular for pumping difficult-to-pump fluid materials, like minerals, ores, sludges, suspensions, slurries, and gels. These pumping machines may be referred to herein simply as pumps or machines.
  • WO 2005/119063 discloses a hydraulically driven multicylinder diaphragm pumping machine, in particular for pumping difficult-to-pump materials.
  • This pumping machine comprises a plurality of pump cylinders each having one end with an inlet and outlet for fluid to be pumped and another end with an inlet and outlet for hydraulic fluid.
  • These inlets and outlets can be a separate inlet and outlet (for the hydraulic fluid) or a combined inlet/outlet (for the fluid material being pumped).
  • the inlets and outlets are associated with respective inlet and outlet valves.
  • a separator is located inside and is movable to-and-fro along each pump cylinder.
  • the movable separator has one side facing the pumped-material end of the cylinder and another side facing the hydraulic-fluid end of the cylinder.
  • This movable separator is connected to the inside of the pumped-material end of the cylinder by a first flexible diaphragm in the form of a concertina-like bellows that is expandable and contractable inside the cylinder along the length direction of the cylinder as the movable separator moves to-and-fro along the cylinder.
  • the movable separator delimits a first chamber inside the first bellows-like flexible diaphragm for containing a variable volume of pumped fluid in communication via the inlet and outlet with a pumped fluid manifold and circuit.
  • the movable separator is connected also to the inside of the second end of the cylinder by a second flexible diaphragm in the form of a concertina-like bellows that is contractable and expandable along the length direction of the cylinder in correspondence with expansion and contraction of the first flexible diaphragm.
  • the second side of the movable separator delimits a second chamber inside the second expandable and contractable diaphragm for containing a variable volume of hydraulic fluid in communication with the second inlet and outlet.
  • An annular space is defined between the outside of the first and second diaphragms and the inner wall of the pump cylinder which annular space in use contains a fluid that is the same as said hydraulic fluid or has similar hydraulic characteristics.
  • This pumping machine is directly driven by a hydraulic pump drive, greatly simplifying the machine and providing simple means of variation and control of the flow of the pumped fluid delivered. Moreover, the double diaphragm arrangement provides a double protection of the pumped fluid from the pumping fluid.
  • This invention aims to improve a machine of the above-mentioned type or more generally other hydraulically-operated machines.
  • One aspect of the invention relates to an improvement of the hydraulic machine as set out above wherein the movable separator is in the form of a plunger that is slidably mounted inside a middle part of the inside of the cylinder between the first and second bellows-like diaphragms, one end of the plunger being connected to the first bellows-like diaphragm and the other end of the plunger being connected to the second bellows-like diaphragm to define respective first and second annular spaces, namely a first annular space between the outside of the first bellows-like diaphragm and the inner wall of the pump cylinder and a second annular space between the outside of the second bellows-like diaphragm and the inner wall of the pump cylinder, wherein the first and second annular spaces are independent of one another and the pressure of fluid in the first annular space is independent of the pressure of fluid in the second annular space.
  • the plunger is slidably mounted in a sealing element secured inside a middle part of the inside of the cylinder.
  • the outer diameter of the plunger corresponds to the median working diameter of the first and second bellows-like diaphragms and the volume of the first and second spaces remains essentially constant during operation.
  • a hydraulic machine - in particular a machine as set out above or generally any other hydraulic machine - comprising a hydraulic cylinder having a part mounted for cyclic reciprocating linear motion along the hydraulic cylinder, and means for commutating a valve to control the supply of hydraulic fluid to the hydraulic cylinder at given moments of the machine's cycle
  • the valve commutating means comprises a hydromechanical switch comprising: a linkage for converting linear motion of said machine part into rotary motion; a cam rotatably driven by said linkage; and a spring arranged to be compressed to store energy by rotation of the cam during a stroke of said machine part, and arranged to release its stored energy to commute said valve for controlling the supply of hydraulic fluid to the hydraulic cylinder of the machine when said part reaches it's given positions along the hydraulic cylinder.
  • the spring can be a compression spring mounted on an arm extending from the cam such that, upon rotational drive of the cam by the linkage, the end of the spring adjacent the cam is compressed until the spring reaches an unstable equilibrium point past which the spring releases its stored energy to commute said valve. For example, when the spring releases its stored energy it firstly abruptly drives the cam and after the cam has turned through a given angle the cam rotates a part to commutate the valve.
  • the linkage can be arranged to turn the cam through an angle less than 180° for each stroke of said machine part.
  • the hydraulic machine can be operated without the need for electromagnetically actuated and electronically controlled directional valves and as a result the machine is less complicated and more reliable.
  • This commutation device also relates to any hydraulic cyclical working machine having a linear moving operating part and requiring to be automatically controlled via openings commutation in order to achieve desired working cycle parameters e.g. pressure values, cycle phases duration, etc.
  • the two principal improvements of the invention relate, on the one hand, to a plunger device to provide fluids separation and, on the other hand, to a hydromechanical switch, it being understood that these two aspects can be incorporated individually or together in a hydraulically driven pumping machine.
  • the hydraulically driven pumping machine shown in Fig. 1 comprises one or several cylinders 5, a switching control system 1 and a hydraulic drive unit 3.
  • the machine is normally a multicylinder machine and such basic hydraulic multicylinder machine is described in detail in PCT patent application WO 2005/119063 .
  • the pump's cylinder 5 contains two bellows 4 and 10 (see Fig. 2 ) mechanically connected to each other via a plunger 6 which moves during the working cycle inside a ring-shaped sealing element 7 mounted in the middle-height part of the cylinder 5.
  • the plunger-sealing assembly 6/7 replaces the separator employed in the previous design.
  • Two oil-filled "a” cavities are located externally of the bellows 4 and 10 inside the cylinder 5.
  • the plunger 6 is hydraulically obturated in the sealing element 7. This allows keeping each of the "a” cavities volume independent from each other.
  • the plunger outside diameter is also equal to the average efficient diameter of the bellows. This allows keeping each of the "a” cavities volume constant during the plunger working movement. Therefore, the pressure values in each of the bellow's external "a"-cavities is exactly piloted by pressure value in the corresponding bellow's internal cavity "b" or "c".
  • the pressure in the internal bellows cavities “b” and “c” varies between the suction and discharge cycles and it depends on the machine working mode.
  • the "b” cavity is located inside the bellows-like membrane 10 and the “c” cavity is located inside the bellows-like membrane 4.
  • the "b" and “c” cavities pressure values are nearly equal, since the driving cavity pressure is transmitted to the driven cavity through the plunger 6 cover.
  • the "c" cavity is driving, the "b" - cavity is driven; and vice versa during the discharge stroke.
  • the hydraulic pressure must enter the machine under sufficient pressure to overcome the mechanical and hydraulic resistances, as the machine does not have any mechanical means to effect the suction stroke.
  • a small part of the driving cavity energy is always consumed by the above mentioned switching device and by other hydraulic and mechanic resistances, therefore, a small pressure drop arises between these "b” and "c” cavities.
  • the pressure drop between the "b” and “c” cavities is not equilibrated via "a"-cavities, because the latter are not connected together hydraulically.
  • the pressure in the "b” and “c” cavities always acts on fluid in the two independent “a” cavities via the bellows wall.
  • the corresponding pressure in the "a” cavities compensates this action precisely and independently balances the pressure values acting on the inner and outer bellows surfaces. The achieved balance eliminates radial deformation and greatly improves the bellows life.
  • the "a" cavities pressure increases to the minimal necessary value, which is sufficient to avoid radial deformation of the bellows wall due to the fluid's low compressibility. This pressure does not depend on the pressure differential between the "b" and “c” cavities, which acts only on the upper and lower surfaces of plunger 6.
  • the arrangement according to the invention eliminates additional radial deformation of the bellows, which would inevitably arise in the previous design that has a conjoint "a" cavity.
  • Another advantage of the inventive solution is improved protection of the pumping fluid from the pumped fluid and vice versa.
  • the previous design could lead to the fluids becoming mixed and corresponding machine malfunction in case of two cavities becoming non-fluid-tight in series: namely cavity "b" and conjoint cavity "a".
  • the present solution has two independent "a” cavities and thus adds one more cavity in this series. It presents, thereby, a triple fluid protection instead of double.
  • the described pump operates as follows (see Fig.2 ):
  • the bellows 4 internal “c” cavity is fed by the pumped material from intake manifold 8 through lower valves module 9.
  • the material is pumped at a small pressure (for example 3-8 bar) that moves the plunger 6 upwards.
  • the bellows 4 is stretched and bellows 10 is compressed which leads to the pumping hydraulic fluid being displaced from cavity "b" into the hydraulic driving system suction manifold.
  • the pressure of the pumped material acting in the 'c" cavity on the bellows 4 internal surface is balanced by a corresponding increase in the fluid pressure in cavity "a” which acts on the bellows 4 external surface.
  • the pressure increase in cavity "b” is balanced by the increase in fluid pressure in the bellows 10 external "a” cavity.
  • the control system 1 switches, and pumping hydraulic fluid supplied by hydraulic drive under high pressure (for example 200 bar) is fed into the bellows 10 "b" cavity. This moves the plunger 6 downward, which generates the discharge stroke. During the discharge stroke the bellows 10 is stretched and bellows 4 is compressed. In a corresponding manner to before, the pressure in cavities “b” and “c” (which is now increasing) is balanced by means of the pressure (which increases) in the two independent cavities "a”, which prevents radial deformation of the bellows 4,10 during the whole discharge stroke. The compressed pumped material is displaced from the "c" cavity through the valves module 8 into the discharge manifold 11. At the end of the discharge stroke the control system 1 switches again, and the machine working cycle starts from the beginning.
  • high pressure for example 200 bar
  • Electromagnetically driven and electronically controlled directional valves are conventionally employed to control cyclic operations of hydraulic machines and mechanisms. These multilevel, sophisticated control systems complicate the hydraulic machines and decrease their reliability.
  • the invention proposes a new device or "hydromechanical switch" to simplify the control systems and increase the reliability of such class of machines.
  • this hydromechanical switch the hydraulic openings are commutated only by mechanical means, without electronic or magnetic appliances.
  • Use of the hydromechanical switch is capable of broadening a controlled machine's area of application in severe environmental conditions, and reduces and simplifies maintenance, staff training, etc.
  • the hydromechanical switch of Figs. 3 to 5 is applicable in general to any hydraulic machine comprising a hydraulic cylinder 107 having a part namely a piston 106 mounted for cyclic reciprocating linear motion along the hydraulic cylinder 107, and means for commutating a valve 102 to control the supply of hydraulic fluid to the hydraulic cylinder at given moments of the machine's cycle.
  • the hydromechanical switch comprises a linkage (screw nut 108, screw rod 109) for converting linear motion of the piston 106 into rotary motion; a cam 103 rotatably driven by said linkage; and a spring 115 arranged to be compressed to store energy by rotation of the cam 103 during a stroke of the piston 106.
  • Spring 115 has one end near the cam 103 and another free end that bears against a flange 114. This spring 115 is moreover arranged to release its stored energy to commute the valve 102 for controlling the supply of hydraulic fluid to the hydraulic cylinder 107 of the machine when the piston 106 is at given positions along the hydraulic cylinder 107.
  • the spring 115 is a compression spring mounted on an arm 150 ( Fig. 2 ) extending from the cam 103 such that, on rotational drive of the cam 103 by the linkage (108,109), the end of the spring adjacent the cam is compressed until the spring reaches an unstable equilibrium point "A" past which the spring releases its stored energy to commute said valve 102.
  • the spring 115 releases its stored energy it firstly abruptly drives the cam 103 through a given angle (say 45°) and then as the cam 103 continues to rotate, it rotates a part to commutate the valve 102 by turning it through, say, 45°.
  • Said linkage (108,109) is arranged to turn the cam through an angle less than 180° for each stroke of the piston 106. It comprises, for instance, the screw nut 108 and the screw rod 109 forming the screw gear linkage.
  • the working principle of the inventive hydromechanical switch is based on the consumption of a part of the machine's linear movement energy. A small portion of this energy is taken away via a screw gear and stored in the spring 115's elastic deformation energy. This stored energy is then released to produce the necessary openings / commutations at given moments of the machine's working cycle.
  • the hydromechanical switch may be designed in the form of a rotating cylindrical valve (see Fig. 3 ), which comprises immobile housing 101, rotating valve body 102, cam 103, driving spring 115 and screw-gear (108,109) for transforming linear motion of piston 106 into rotational motion of the cam 103.
  • said part mounted for cyclic reciprocating movement along the cylinder is the piston 106 or a plunger or other part fixed thereto.
  • the illustrated hydromechanical switch operates as follows.
  • nut 108 is also moving. This motion causes rotation of the screw rod 109.
  • the screw rod's axial motion is disabled via bearing and sealing unit 111.
  • Another purpose of the unit 111 is to hold the screw 109 fluid-tightly inside the cover 110.
  • the screw shaft 112 rotates the cam 103 through pin 113 and the finger 104. Compression of spring 115 occurs simultaneously with rotation of the cam 103.
  • the spring pivots also about its free end and reaches an unstable equilibrium state point "A" at the end of the piston stroke. This unstable equilibrium point corresponds to the maximum compression of the spring 115, when the lateral axis of the spring 115 intersects the rotation axis of the cam 103, i.e.
  • Fig 5 shows the spring laterally offset from the equilibrium position, with the spring 115 in a less-compressed state at the beginning of its compression stroke, ready to start turning.
  • a ball-fastener 119 is designed to limit rotation of the valve in extreme positions. The valve comes against the stop 120 and is fixed by the ball-fastener 119 at the end of the turn.
  • the cog 117 is equipped with a rubber damper 121 to minimize shock upon contact of the stud 118 and stop 120.
  • the rotating valve 102 is statically and dynamically hydraulically balanced to compensate radial pressure components that otherwise would cause undue friction during the valve's rotation..
  • the spring 115's compression occurs during the whole piston stroke to evenly consume it's energy.
  • the spring is soft and has corresponding low resistance variation over the stroke.
  • the circular surface "B" of the pin 113 is sustained by balancing pressure directed from the internal cylinder's cavity through a special channel, and the surface "B" area is equal to the shaft's 112 sectional area to balance the pulling force, which acts on the screw 109 by reason of the internal cylinder's pressure.
  • the hydromechanical switch is equipped with an indicator 122 to observe the valve and the piston positions, motion direction, velocity and operation.
  • an indicator 122 to observe the valve and the piston positions, motion direction, velocity and operation.
  • any angular sensors may be employed to monitor the machine operation electronically, if required.
  • Involute splines 124 and 125 on the cam's shaft are designed to adjust the piston stroke and the indicator pointer 123 position during the assembly process.
  • Bolts 126 are designed to produce a fine tune of the cam 103 rotation angle and the whole hydromechanical switch operation.
  • a tunable junction 127 is designed to adjust the spring 115's performance.
  • the hydromechanical switch operates automatically, i.e. the working machine commands itself. For example, if the piston velocity changes, the valve commutation still continues to happen at the right time, because the commutation process depends only on the piston position, not on velocity nor on acceleration.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
EP08163603.7A 2007-01-19 2007-01-19 Verbesserung für eine hydraulisch angetriebene Maschine Active EP2009283B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP08163603.7A EP2009283B1 (de) 2007-01-19 2007-01-19 Verbesserung für eine hydraulisch angetriebene Maschine

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
EP08163603.7A EP2009283B1 (de) 2007-01-19 2007-01-19 Verbesserung für eine hydraulisch angetriebene Maschine
EP07100835A EP1947331A1 (de) 2007-01-19 2007-01-19 Verbesserung für eine hydraulisch angetriebene Maschine

Related Parent Applications (2)

Application Number Title Priority Date Filing Date
EP07100835A Division EP1947331A1 (de) 2007-01-19 2007-01-19 Verbesserung für eine hydraulisch angetriebene Maschine
EP07100835A Previously-Filed-Application EP1947331A1 (de) 2007-01-19 2007-01-19 Verbesserung für eine hydraulisch angetriebene Maschine

Publications (3)

Publication Number Publication Date
EP2009283A2 true EP2009283A2 (de) 2008-12-31
EP2009283A3 EP2009283A3 (de) 2009-04-29
EP2009283B1 EP2009283B1 (de) 2016-03-23

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Family Applications (2)

Application Number Title Priority Date Filing Date
EP07100835A Withdrawn EP1947331A1 (de) 2007-01-19 2007-01-19 Verbesserung für eine hydraulisch angetriebene Maschine
EP08163603.7A Active EP2009283B1 (de) 2007-01-19 2007-01-19 Verbesserung für eine hydraulisch angetriebene Maschine

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Application Number Title Priority Date Filing Date
EP07100835A Withdrawn EP1947331A1 (de) 2007-01-19 2007-01-19 Verbesserung für eine hydraulisch angetriebene Maschine

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Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8591201B2 (en) 2008-03-20 2013-11-26 Garniman S.A. Hydraulically driven machine improvement
CN114033128A (zh) * 2021-11-18 2022-02-11 广东博智林机器人有限公司 输料过渡机构、泵送装置及喷涂设备
CN116538060B (zh) * 2023-06-02 2024-01-30 深圳市益思精密五金有限公司 一种分布式折叠隔膜泵
CN117759579A (zh) * 2023-12-15 2024-03-26 安徽铜都流体科技股份有限公司 一种双向蓄能装置、液压换向系统及方法

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US862867A (en) * 1906-03-28 1907-08-06 Lewis Watson Eggleston Pneumatic pumping apparatus.
US3182597A (en) * 1962-04-21 1965-05-11 Malizard Max Proportioning pump
DE1653445A1 (de) * 1967-06-14 1971-07-22 Erich Goldbecker Doppeltwirkende Pumpe
GB1574278A (en) * 1978-05-09 1980-09-03 Berelson R Additive pumping unit for liquids
WO2005119063A1 (en) * 2004-06-02 2005-12-15 Garniman Sa Hydraulically driven multicylinder pumping machine

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2675787A (en) * 1954-04-20 Fluid meter
US2268898A (en) * 1938-05-06 1942-01-06 Us Air Compressor Company Fluid motor
US2604879A (en) * 1945-08-13 1952-07-29 King Seeley Corp Reciprocating piston type fluid motor
US2521566A (en) * 1946-05-09 1950-09-05 Marquette Metal Products Co Fluid operated reciprocating motor with rotary reversing valve
US2607324A (en) * 1947-10-17 1952-08-19 Theodore E Mead Pressure fluid motor control
US3597120A (en) * 1969-05-14 1971-08-03 John H Reed Injector-recirculation pump

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US862867A (en) * 1906-03-28 1907-08-06 Lewis Watson Eggleston Pneumatic pumping apparatus.
US3182597A (en) * 1962-04-21 1965-05-11 Malizard Max Proportioning pump
DE1653445A1 (de) * 1967-06-14 1971-07-22 Erich Goldbecker Doppeltwirkende Pumpe
GB1574278A (en) * 1978-05-09 1980-09-03 Berelson R Additive pumping unit for liquids
WO2005119063A1 (en) * 2004-06-02 2005-12-15 Garniman Sa Hydraulically driven multicylinder pumping machine

Also Published As

Publication number Publication date
EP1947331A1 (de) 2008-07-23
EP2009283B1 (de) 2016-03-23
EP2009283A3 (de) 2009-04-29

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