EP2921700A1 - Machine hydrostatique à piston radial dotée de trois raccords hydrauliques et fenêtres de commande destinées à commander un vérin différentiel - Google Patents

Machine hydrostatique à piston radial dotée de trois raccords hydrauliques et fenêtres de commande destinées à commander un vérin différentiel Download PDF

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Publication number
EP2921700A1
EP2921700A1 EP14161072.5A EP14161072A EP2921700A1 EP 2921700 A1 EP2921700 A1 EP 2921700A1 EP 14161072 A EP14161072 A EP 14161072A EP 2921700 A1 EP2921700 A1 EP 2921700A1
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EP
European Patent Office
Prior art keywords
port
working
hydrostatic machine
differential cylinder
control
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.)
Withdrawn
Application number
EP14161072.5A
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German (de)
English (en)
Inventor
Dirk Becher
Tino Kentschke
Achim Helbig
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.)
Moog GmbH
Original Assignee
Moog GmbH
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 Moog GmbH filed Critical Moog GmbH
Priority to EP14161072.5A priority Critical patent/EP2921700A1/fr
Priority to CN201580009813.XA priority patent/CN106103987A/zh
Priority to PCT/EP2015/055461 priority patent/WO2015140116A1/fr
Priority to US15/127,673 priority patent/US20170138335A1/en
Publication of EP2921700A1 publication Critical patent/EP2921700A1/fr
Withdrawn legal-status Critical Current

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    • 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
    • F03C1/02—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders
    • F03C1/04—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinders in star or fan arrangement
    • F03C1/0403—Details, component parts specially adapted of such engines
    • F03C1/0435—Particularities relating to the distribution members
    • F03C1/0438—Particularities relating to the distribution members to cylindrical distribution members
    • 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
    • F03C1/02—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders
    • F03C1/04—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinders in star or fan arrangement
    • F03C1/0403—Details, component parts specially adapted of such engines
    • F03C1/0435—Particularities relating to the distribution members
    • F03C1/0441—Particularities relating to the distribution members to conical distribution members
    • 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
    • F03C1/02—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders
    • F03C1/04—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinders in star or fan arrangement
    • F03C1/0447—Controlling
    • F03C1/045—Controlling by using a valve in a system with several pump or motor chambers, wherein the flow path through the chambers can be changed, e.g. series-parallel
    • 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
    • F03C1/02—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders
    • F03C1/04—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinders in star or fan arrangement
    • F03C1/047—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinders in star or fan arrangement the pistons co-operating with an actuated element at the outer ends of the cylinders
    • 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
    • F03C1/02—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders
    • F03C1/04—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinders in star or fan arrangement
    • F03C1/053—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinders in star or fan arrangement the pistons co-operating with an actuated element at the inner ends of the 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
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/0404—Details or component parts
    • F04B1/0452—Distribution members, e.g. valves
    • F04B1/0456—Cylindrical
    • 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
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/0404—Details or component parts
    • F04B1/0452—Distribution members, e.g. valves
    • F04B1/0461—Conical
    • 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
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/047—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement with actuating or actuated elements at the outer ends of the 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
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/053—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement with actuating or actuated elements at the inner ends of the 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
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/06—Control
    • F04B1/063—Control by using a valve in a system with several pumping chambers wherein the flow-path through the chambers can be changed, e.g. between series and parallel flow
    • 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
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/08—Servomotor systems without provision for follow-up action; Circuits therefor with only one servomotor
    • F15B11/10—Servomotor systems without provision for follow-up action; Circuits therefor with only one servomotor in which the servomotor position is a function of the pressure also pressure regulators as operating means for such systems, the device itself may be a position indicating system
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
    • F15B2211/7051—Linear output members
    • F15B2211/7053—Double-acting output members

Definitions

  • the invention relates to a hydrostatic radial piston machine, in particular a hydrostatic radial piston machine for controlling a differential cylinder.
  • Generic hydrostatic radial piston machines are used in many types of industrial applications.
  • generic hydrostatic radial piston machines can be found in machines for injection and pressure casting processes, systems of the forming technology, such as, for example, Presses, rolling mills and in general hydraulic aggregate construction.
  • the drive torque is transmitted from the shaft to a cylinder star which is mounted on a control pin.
  • Pistons arranged radially in the cylinder star are supported by sliding shoes in a lifting ring.
  • the shoes can be hydrostatically relieved in a suitable manner.
  • Piston and shoe are connected by a joint and tied by a ring.
  • the sliding shoes are guided through two overlapping rings in the lifting ring and pressed by centrifugal force and oil pressure to the cam ring during operation.
  • the pistons due to the eccentric position of the cam ring perform a stroke movement, which corresponds to twice the value of the eccentricity.
  • the eccentricity can be changed by two opposite in the pump housing actuator piston.
  • the oil flow is fed in and out via ducts in the housing and control spigots. This is controlled by means of suction and pressure windows in the control pin. By means of a regulator, the stroke ring position (flow rate) or the system pressure can be controlled.
  • a differential cylinder to be driven via a hydrostatic radial piston engine usually proportional or control valves are interposed. Differential cylinders have two working spaces, each with a working port, wherein a first working port to the working space on the piston side and a second working connection to the working space on the rod side of the differential cylinder lead.
  • the volumetric flow of the hydraulic fluid provided by the hydrostatic radial piston machine can be supplied to the respective working connection and thus to the respective working space via the valves.
  • the displacement units can be provided on a drive shaft, wherein the drive shaft is usually connected to an electric motor, which is typically operated at variable speed and direction of rotation. Another characteristic is that the speed of the electric motor is constant and are operated on the drive shaft, two displacement units with variable displacement.
  • this involves the disadvantage that two displacement units are needed and thus high costs arise.
  • the object of the invention is to provide a device with which a differential cylinder using a single hydrostatic machine directly, in particular without the interposition of proportional or control valves, is operable, the device should be inexpensive to implement and only takes up a small space. It is another object of the invention to provide a hydraulic actuator as a corresponding system.
  • the radial-piston hydrostatic machine has a displacer unit, wherein the displacer unit is driven by a drive motor and wherein the hydrostatic machine further comprises a housing in which a control pin is arranged, wherein the hydrostatic machine has at least three hydraulic working connections.
  • the first working port may be connected to the working port of the piston side of a differential cylinder, while the second working port may be connected to the working port of the rod side of the differential cylinder.
  • the third working connection can be connected to a tank.
  • the differential cylinder is directly operable by means of a single hydrostatic machine, which can be dispensed with the interposition of proportional or control valves.
  • the device is inexpensive to implement and takes up little space to complete.
  • the drive motor can be in particular an electric motor.
  • control pin has a first work-side control window which is connected to a first work connection A, a second work-side control window; which is connected to a second working port B, and a third control window which is connected to a third working port T comprises.
  • the control pin has suction-side control windows.
  • the control pin have Um Tavernkerben on all control windows.
  • the second working-side control window has a smaller cross-section than the first working-side control window.
  • the third work-side control window also has a smaller cross-section than the first working-side control window, whereby only a part of the pumped from or into the piston side hydraulic fluid can be discharged into the tank or can be nachgesogen from this.
  • the ratio of the first and second operating side control windows on the area ratio of the effective areas of the piston from the piston side and rod side of the differential cylinder can be tuned.
  • the area ratio of the effective areas of the piston can be impressed from the piston side and rod side of the differential cylinder via a corresponding design of the control window in the control pin.
  • the area ratio of the effective areas of the piston from the piston side and the rod side of the differential cylinder corresponds to the ratio of the working space volumes of the piston side and the rod side of the differential cylinder.
  • a volumetric flow balance can be set up on the displacer unit, in which the volumetric flow at the working connection to the piston-side working space of the differential cylinder is equal to the sum of the volume flows to the rod-side working space of the differential cylinder and to the tank.
  • the volume flow into a working chamber of the differential cylinder corresponds to the product of the piston rod speed of the differential cylinder with the respective effective piston area of the differential cylinder.
  • the individual volume flows can be calculated at the working ports of the displacer unit, wherein these flow rates correspond to those in the respective working spaces of the differential cylinder or in the tank.
  • the volume flow at the working connection to the piston-side working space of the differential cylinder corresponds to the rotational speed of the displacer unit multiplied by the geometrically embossed volume in the displacer unit on the first operating control window and thus the product of the rotational speed of the displacer unit with the square of the Hubkolben pressmessers, the eccentricity, the number of reciprocating and half of the circle number ⁇ as a constant.
  • the volume flow at the working connection to the rod-side working space of the differential cylinder corresponds to the rotational speed of the displacer unit multiplied by the geometrically embossed volume in the displacer unit on the second operating control window and thus the product of the rotational speed of the displacer unit with the square of the Hubkolben pressmessers, the eccentricity, the number of reciprocating and half of the circle number ⁇ as a constant divided by the ratio of the effective piston area of the differential cylinder, ie the product of the speed of the displacement unit and the volume flow at the working port to the piston-side working space of the differential cylinder, divided by the ratio of the effective piston surfaces of the differential cylinder.
  • the volume flow at the working connection to the tank corresponds to the speed of the displacer unit multiplied by the volume of the piston-side working space of the differential cylinder and the difference of 1 and the reciprocal of the ratio of the effective piston areas of the differential cylinder.
  • Entry and exit direction of the piston rod in or out of the differential cylinder are controlled by the direction of rotation of the motor.
  • the left-hand rotation of the motor corresponds to the extension of the piston rod, while the clockwise rotation of the motor corresponds to retraction.
  • control pin is firmly connected to the housing.
  • the housing likewise has three working connections which establish the connection to the two working connections of the differential cylinder and to the tank.
  • the second control window port B is formed by two sub-control windows port B1 and B2, wherein the sub-control windows are connected to the working port B and seen in the circumferential direction of the control pin, the third control window between the sub-control windows port B1 and B2 port.
  • the third Control window port T formed by two sub-control windows port T1 and port T2, wherein the sub-control windows are connected to the working terminal T and seen in the circumferential direction of the control pin, the second control window Port B between the sub-control windows Port T1 and T2 port.
  • the hydrostatic machine has an additional hydraulic connection, via which accumulating leak oil can be discharged.
  • the hydrostatic machine may be a fixed displacement pump in which the displacement volume is constant.
  • the hydrostatic machine can also have an adjusting device, via which their displacement volume is adjustable.
  • An inventive hydraulic actuator for controlling a differential cylinder has the differential cylinder itself, a tank and a hydrostatic machine according to the invention.
  • the first working port A of the hydrostatic machine is connected to the working port of the piston side of the differential cylinder, the second working port B of the hydrostatic machine to the working port of the rod side of the differential cylinder, while the third working port T of the hydrostatic machine is connected to the tank.
  • the tank has a check valve, via which it is connected to the first working port A of the hydrostatic machine and / or the second working port B of the hydrostatic machine.
  • Fig. 1 shows a displacer unit 110 in the form of a radial piston pump in a sectional view, as known from the prior art.
  • the drive torque is transmitted by a shaft via a clutch without transverse force on the cylinder star 111, which is mounted on the control pin 120.
  • the lifting pistons 112 arranged radially in the cylinder star 111 are supported via hydrostatically relieved sliding shoes 113 in the lifting ring 114. Hubkolben 112 and shoe 113 are connected to each other via a ball joint and tied by a ring.
  • the sliding blocks are guided by two overlapping rings 115 in the cam ring 114 and pressed in operation by centrifugal force and oil pressure to the cam ring 114.
  • the reciprocating piston 112 due to the eccentric position of the cam ring 114 perform a lifting movement, which corresponds to twice the value of the eccentricity.
  • the eccentricity is changed by two in the pump housing 130 opposite actuating piston 116.
  • the oil flow is supplied and discharged via channels in housing 130 and control pin 120. This is controlled by means of suction and pressure windows (ports) in the control pin 120.
  • a controller 117 controls the stroke ring position and thus the flow rate or the system pressure.
  • Fig. 2 shows a schematic diagram of a differential cylinder 140 of the prior art, which is driven by two hydrostatic displacement units 110.
  • the two hydrostatic displacement units 110 are variable displacement pumps, which are arranged on a motor shaft, which is driven by a motor M.
  • the engine M may be an electric motor, but the use of other engines such as internal combustion engines is also possible.
  • the differential cylinder 140 has a piston-side working space R A and a rod-side working space R B , which via a working port 143 on the Piston side of the differential cylinder or a working port 144 on the rod side of the differential cylinder can be acted upon with hydraulic fluid.
  • a second displacer unit 110 is provided to compensate for the hydraulic volume during movement of the differential cylinder 140, depending on the direction of movement of the differential cylinder 140 Hydrualikfluid from a tank 160 in the working space R A promote or can pump out of the working space R A in the tank 160 ,
  • Fig. 3 shows a control pin 120 in three-dimensional view from a first perspective. From this perspective, the first control window Port A is visible. The first control window Port A is connected to a first connection window 121 via a bore running inside the control pin 120. Via the first connection window 121, the first control window Port A is connected to the working port A of the hydrostatic machine 100.
  • Fig. 4 shows the control pin 120 in three-dimensional view from a second perspective, which is about 180 ° about the axis of rotation relative to the view Fig. 3 in which the second control window Port B and the third control window Port T are visible.
  • the second control window Port B is connected to a second connection window 122 via a bore extending within the control pin 120.
  • the second control window port B is connected to the working port B of the hydrostatic machine 100 via the second connection window.
  • the third control window Port T is connected to a third port window 123 via a bore extending inside the control pin 120. Via the third connection window 123, the third control window Port T is connected to the working connection T of the hydrostatic machine 100.
  • the first control window Port A is connected to the piston side R A of the differential cylinder 140, while the second control window Port B is connected to the rod side R B of the differential cylinder 140.
  • the third control window port T is connected to a tank 160.
  • the second control window Port B has a smaller cross-section than the first control window port A.
  • the ratio between the first control window Port A and second control window port B corresponds to the ratio of the effective piston areas in the piston-side working space R A and the rod-side working space R B of the differential cylinder 140.
  • the third control window Port T also has a smaller cross-section than the first control window port A, whereby only a part of the pumped out of or in the piston side hydraulic fluid can be discharged into the tank or nachgesogen from the tank.
  • control pin In addition to the working side, that is to say pressure-side control windows, the control pin has suction-side control windows. In this case, the control pin have Um Tavernkerben on all control windows.
  • the area ratio ⁇ of the effective areas A RA and A RB of the piston of piston side R A and rod side R B of the differential cylinder 140 is impressed on the control pin 120 via a kidney-shaped design of the control window Port A, Port B, Port T.
  • Fig. 5 shows a schematic diagram of a hydrostatic radial piston machine 100 according to the invention with control of a differential cylinder 140.
  • the hydrostatic radial piston machine has a direction of rotation and variable speed motor M and a driven by him radial piston pump 110.
  • the differential cylinder 140 has a piston with a piston rod and the corresponding work spaces R A , R B.
  • the effective piston area A RB on the rod side R B is reduced by the piston rod with respect to the effective piston area A RA on the piston side R A.
  • the working spaces R A and R B are connected via working ports 143, 144 with the working ports A, B of the radial piston pump 110 so that when the motor M is running to the left, the piston rod extends, while the right-hand motor retracts the piston rod into the differential cylinder 140, wherein the retraction by a dashed arrow and the extension direction is indicated by a dotted arrow.
  • the arrows on the Working lines designate the volume flows Q A in or out of the piston-side working space R A of the differential cylinder 140, Q B in or out of the rod-side working space R B of the differential cylinder 140 and out of the tank Q T.
  • the solid arrows indicate the flow direction of the hydraulic fluid for the extension movement of the piston rod from the differential cylinder 140
  • the dashed arrows indicate the flow direction of the hydraulic fluid for the retraction movement of the piston rod of the differential cylinder 140.
  • the piston rod moves out of the differential cylinder 140 at the speed v L or into the differential cylinder 140 at the speed v R.
  • a volumetric flow balance can be set up on the displacer unit 110, in which the volume flow Q A at the working port A to the piston-side working space R A of the differential cylinder 140 equal to the sum of the volume flows Q B , Q T to the rod-side working space R B of the differential cylinder 140 and to the prestressed Tank is 160.
  • the volume flow Q RA , Q RB into a working space R A , R B of the differential cylinder 140 corresponds to the product of the piston rod speed v of the differential cylinder 140 with the respective effective piston area A RA , A RB of the differential cylinder 140:
  • the individual volume flows Q A , Q B , Q T can be calculated at the working ports A, B, T of the radial piston pump 110, wherein these flow rates Q A , Q B , Q T those in the respective working chambers R A , R B of the differential cylinder or correspond to the tank 160.
  • the volume flow Q A at the working port A to the piston-side working chamber R A of the differential cylinder 140 corresponds to the rotational speed n of the radial piston pump 110 multiplied by the volume V A geometrically embossed in the displacer unit on the first working-side control port Port A and thus the product of rotational speed n of the radial piston pump 110 with the square of Hubkolben pressmessers D, the eccentricity e, the number of reciprocating piston z and the half of the circle number ⁇ as Constant:
  • the volume flow Q B at the working port B to the rod-side working chamber R B of the differential cylinder 140 corresponds to the rotational speed n of the radial piston pump 110 multiplied by in the displacer unit on the second working side port window port B geometrically embossed volume V B and thus the product of speed n of the radial piston pump 110 with the square of Hubkolben pressmessers D, the eccentricity e, the number z of the reciprocating piston and half the circle number ⁇ as a constant divided by the ratio of the effective piston areas A RA , A RB of the differential cylinder 140, ie the product of speed n of the radial piston pump 110 and the Volume flow Q RA at the working port 143 to the piston-side working space R A of the differential cylinder 140 divided by the ratio ⁇ of the effective piston surfaces A RA , A RB of the differential cylinder 140:
  • the delivery volume of the radial piston pump at an area ratio ⁇ from the effective area A RA of the piston side R A to the effective area A RB of the rod side R B is 1.5: 1 at the working port A 18 cm 3 , at the working port B 12 cm 3 and at the working connection T 6cm 3 per revolution.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Reciprocating Pumps (AREA)
  • Hydraulic Motors (AREA)
  • Details Of Reciprocating Pumps (AREA)
EP14161072.5A 2014-03-21 2014-03-21 Machine hydrostatique à piston radial dotée de trois raccords hydrauliques et fenêtres de commande destinées à commander un vérin différentiel Withdrawn EP2921700A1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
EP14161072.5A EP2921700A1 (fr) 2014-03-21 2014-03-21 Machine hydrostatique à piston radial dotée de trois raccords hydrauliques et fenêtres de commande destinées à commander un vérin différentiel
CN201580009813.XA CN106103987A (zh) 2014-03-21 2015-03-16 静压径向活塞式机械
PCT/EP2015/055461 WO2015140116A1 (fr) 2014-03-21 2015-03-16 Machine hydrostatique à pistons radiaux
US15/127,673 US20170138335A1 (en) 2014-03-21 2015-03-16 Hydrostatic radial piston machine

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP14161072.5A EP2921700A1 (fr) 2014-03-21 2014-03-21 Machine hydrostatique à piston radial dotée de trois raccords hydrauliques et fenêtres de commande destinées à commander un vérin différentiel

Publications (1)

Publication Number Publication Date
EP2921700A1 true EP2921700A1 (fr) 2015-09-23

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EP14161072.5A Withdrawn EP2921700A1 (fr) 2014-03-21 2014-03-21 Machine hydrostatique à piston radial dotée de trois raccords hydrauliques et fenêtres de commande destinées à commander un vérin différentiel

Country Status (4)

Country Link
US (1) US20170138335A1 (fr)
EP (1) EP2921700A1 (fr)
CN (1) CN106103987A (fr)
WO (1) WO2015140116A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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WO2021207638A1 (fr) * 2020-04-10 2021-10-14 Moog Inc. Système de pompe à piston électrohydraulique à couple d'assistance
JP2023522176A (ja) * 2020-04-10 2023-05-29 ムーグ インコーポレーテッド 補助トルク電気油圧式ピストン・ポンプ・システム
WO2022234284A1 (fr) * 2021-05-06 2022-11-10 Domin Fluid Power Limited Pompe à piston radial
DE102021113665A1 (de) 2021-05-27 2022-12-01 HMS - Hybrid Motion Solutions GmbH Hydraulisches Antriebssystem
WO2022248153A1 (fr) 2021-05-27 2022-12-01 HMS - Hybrid Motion Solutions GmbH Système d'entraînement hydraulique

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CN106103987A (zh) 2016-11-09
WO2015140116A8 (fr) 2016-02-18
WO2015140116A1 (fr) 2015-09-24

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