EP0005190A1 - Pompe à pistons radiaux - Google Patents

Pompe à pistons radiaux Download PDF

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Publication number
EP0005190A1
EP0005190A1 EP79101096A EP79101096A EP0005190A1 EP 0005190 A1 EP0005190 A1 EP 0005190A1 EP 79101096 A EP79101096 A EP 79101096A EP 79101096 A EP79101096 A EP 79101096A EP 0005190 A1 EP0005190 A1 EP 0005190A1
Authority
EP
European Patent Office
Prior art keywords
pump
valve
pressure
tank
pump elements
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
EP79101096A
Other languages
German (de)
English (en)
Other versions
EP0005190B1 (fr
Inventor
Jörg Dantlgraber
Horst Kramer
Horst Fischer
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.)
Bosch Rexroth AG
Original Assignee
Mannesmann Rexroth AG
GL Rexroth 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 Mannesmann Rexroth AG, GL Rexroth GmbH filed Critical Mannesmann Rexroth AG
Publication of EP0005190A1 publication Critical patent/EP0005190A1/fr
Application granted granted Critical
Publication of EP0005190B1 publication Critical patent/EP0005190B1/fr
Expired legal-status Critical Current

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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
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/22—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves
    • F04B49/24—Bypassing
    • 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

Definitions

  • the invention relates to a radial piston pump with at least two pump elements. If such radial piston pumps are used, for example, for clamping purposes in machine tool construction, after the clamping position or working position of the clamping cylinder has been reached, the entire pump delivery flow must be discharged to the tank via a pressure relief valve in order to maintain the clamping force. This results in an uneconomical operation of the radial piston pumps during the clamping process.
  • the working fluid is appropriately heated by removing the working fluid via a pressure-limiting valve that determines the clamping force and must therefore be cooled back down to the prescribed operating temperature.
  • the object of the invention is to provide a radial piston pump which ensures energy-saving operation with the simplest of means, particularly when used for clamping hydraulics.
  • 1 denotes the pump housing and 2 the pump housing cover.
  • five pressure valve inserts lbl, 1b2, 1b3, 1b4, 1b5 are evenly distributed over the circumference.
  • pump elements 3 each work together, the cylinder body 3a of which is sealingly supported on the receiving body 4 for the pressure valve (not shown).
  • the piston of each pump element 3 is supported with its foot 3b on the running surface of the eccentric 4 of the drive shaft 5, which is supported in slide bearings 6, 7 on both sides of the eccentric.
  • the slide bearing 6 is arranged in a recess in the pump housing and the slide bearing 7 in a corresponding recess in the housing cover 2.
  • the housing space 8 also forms the suction space for the individual pump elements 3 and is connected via the connection 9 to the tank, not shown.
  • a control piston 11 (FIGS. 1 and 2) and a compression spring 12 are arranged in a stepped bore 10 in the housing cover.
  • the compression spring 12 is supported with its one end via the spring plate 13 at one end 11a of the control piston 11 (FIGS. 1 and 2) and with its other end to a spring plate 14, which in turn is supported on a set screw 16 via a bolt 15 .
  • the adjusting screw 16 which determines the spring tension of the spring 12, is secured against rotation by the lock nut 17.
  • the two control piston sections 11b, 11c of the control piston 11 (FIGS.
  • a channel 21 leads to the annular control chamber 18, which is connected to a collecting channel 22, on which four transverse channels 23a, 23b, 24a, 24b are connected.
  • the transverse channels connect via the collecting channel 22, the pressure sides formed by the pressure valve inserts 1b2, 1b5, 1b3, lb4 of the four pump elements assigned to these pressure valve inserts, the collecting channel 22 underneath each other.
  • the pressure valve insert lbl is connected to the control chamber 19 via the channel 26 in the pump housing 1 and via the channel 27 in the pump housing cover 2 connected and is therefore separated from the remaining four pressure valve inserts.
  • control channels 29 and 3o (FIG. 2).
  • the control channel 29 opens into a space 31 which is in direct connection with the tank connection 32.
  • This space 31 is also connected via a bore 33 to the annular space 34 penetrated by the control piston end 11a and this to the spring space 35.
  • the spring space is thus in permanent communication with the tank connection 32.
  • the control channel 3o is in a space delimited by a screw plug 37 38 in connection.
  • This space 38 is in turn connected via a bore 39 to the control chamber 19, which in turn is in direct connection with the pressure connection 20 of the radial piston pump.
  • control piston 11 In the switching position shown in FIG. 2, the control piston 11 is in its starting position, in which the control piston section 11b with control edge 11bk keeps the control bore 29 closed, while the control piston section 11c with control edge 11ck releases the control bore 3o, so that the control chamber 18 via the Control hole 3 0 , the space 38 and the connection bore 39 with the control space 19 and thus with the pressure connection of the pump is in communication.
  • the pressure sides of the pump elements 3 formed by the pressure valve inserts lbl, 1b3, 1b4 and 1b5 are thus also connected to the pressure connection 2o via the channel 21, which is connected to the control chamber 18.
  • the pump element 3 cooperating with the pressure valve insert 1b1 is in permanent connection with the pressure connection 2o via the channels 26 and 27, all pump elements are connected to the pressure connection 2o, so that the total delivery volume of the radial piston pump to the consumer (not shown in more detail), for example a hydraulic cylinder, which is used as a clamping cylinder is available. As soon as the consumer has reached a final position of a clamping cylinder, for example, the consumer pressure rises.
  • the control piston end 11d has a somewhat larger diameter than the control piston section 11c having the control edge 11ck. This creates an abutment surface 11a which defines the switching position shown in FIG. 1.
  • the initial switch position according to FIG. 2 is determined by the spring plate 13, which rests with its support surface 13a on the surface loa of the stepped bore.
  • the changeover valve formed by the stepped bore lo in connection with the control bores, the control piston 11, the control spring 12 and the adjusting screw 16 is integrated in the pump housing cover 2 and the channels 21, 22, 23a, 23b, 24a, 24b the connection of the
  • the pressure valve inserts 1b2, 1b3, lb4 and lb5 are operatively connected to pump elements. This results in a particularly compact unit that guarantees an operationally reliable changeover function of the changeover valve even under rough operating conditions.
  • the radial piston pump works in two pressure ranges, namely in a low pressure range and in a high pressure range. The low pressure range results in a switching position of the control piston 11 according to FIG. 2, in which all pump elements are connected to the pressure connection 20.
  • the high-pressure range results from a switching position of the control piston 11 according to FIG. 1, in which only the pump element assigned to the pressure valve insert 1b1 contributes to maintaining the consumer pressure, while the other pump elements are connected to the tank.
  • the exemplary embodiment according to FIG. 3 differs from the exemplary embodiment according to FIGS. 1 and 2 only by the design of the changeover valve 5o and by the additional arrangement of a check valve 51 between the channels 21 and 27.
  • the changeover valve 5o is designed as a two-way seat valve and is formed by the valve seat body 52 designed as a ball, which cooperates with the valve seat 53.
  • the bore section 58 which corresponds to the channel section 34 according to FIG. 2, is likewise connected to the tank connection via a bore 33. In the open switching position of the valve seat body 52, the control chamber 18 is thus connected to the tank connection via the channel section 54 and thus also the pressure sides of part of the pump elements which are connected to the control chamber 18.
  • valve seat body In the closing direction, the valve seat body is loaded by the pretension of the compression spring 12 via the spring plate 13 with the actuating pin 55. In the opening direction, the valve seat body is loaded with the actuating pin 57 by the power piston 56 acted upon by the consumer pressure prevailing in the control chamber 19 via the pressure connection 20. As long as the force exerted by the consumer pressure on the power piston in the opening direction of the valve seat body is smaller than the force directed by the bias of the compression spring 12 in the closing direction of the valve seat body, the connection of the control chamber 18 with the bore section 58 remains interrupted by the shown closed position of the valve seat body.
  • the liquid conveyed through the channel 22 pump elements that are operatively connected to the channel 21 flows into the channel 27 via the check valve 51 and combine there with the delivery liquid of the pump elements that are operatively connected to this channel.
  • the entire delivery liquid flows via the control chamber 19 to the pressure connection 20 and from there to the consumer (not shown), for example a hydraulic motor.
  • the pressure of this conveying fluid flowing to the consumer acts in the control chamber 19 on the power piston 56 in the opening direction of the valve seat body 52.
  • the pressure of the conveying fluid increases to such an extent that the power piston 56 via the actuating pin 57 pushes the valve seat body against the force of the compression spring 12 moves in the opening direction and a connection of the control chamber 18 to the bore portion 58 and thus produces the tank, the pressure of the winningflüssi falls g ness of the connected via the channel 21 with the control chamber 18 pump elements to the tank pressure from, said by the thus resulting pressure gradient in front of and behind the check valve 51, this closes and thus only the delivery liquid of the pump elements connected to the channel 27 is supplied to the consumer or is discharged via a pressure relief valve to the tank if the consumer has hit a stop and a certain force should exercise.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Details Of Reciprocating Pumps (AREA)
  • Reciprocating Pumps (AREA)
  • Control Of Positive-Displacement Pumps (AREA)
EP79101096A 1978-04-20 1979-04-10 Pompe à pistons radiaux Expired EP0005190B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19782817173 DE2817173A1 (de) 1978-04-20 1978-04-20 Radialkolbenpumpe
DE2817173 1978-04-20

Publications (2)

Publication Number Publication Date
EP0005190A1 true EP0005190A1 (fr) 1979-11-14
EP0005190B1 EP0005190B1 (fr) 1981-12-02

Family

ID=6037507

Family Applications (1)

Application Number Title Priority Date Filing Date
EP79101096A Expired EP0005190B1 (fr) 1978-04-20 1979-04-10 Pompe à pistons radiaux

Country Status (5)

Country Link
US (1) US4257750A (fr)
EP (1) EP0005190B1 (fr)
JP (1) JPS54141405A (fr)
AT (1) AT361301B (fr)
DE (1) DE2817173A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0428374A1 (fr) * 1989-11-13 1991-05-22 Hobourn Automotive Limited Systèmes de pompe à déplacement positif

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4690620A (en) * 1980-08-19 1987-09-01 Karl Eickmann Variable radial piston pump
US4551069A (en) * 1984-03-14 1985-11-05 Copeland Corporation Integral oil pressure sensor
DE3513164A1 (de) * 1985-04-12 1986-10-23 Robert Bosch Gmbh, 7000 Stuttgart Radialkolbenpumpe
DE19805138B4 (de) * 1998-02-09 2006-07-06 Kriwan Industrie-Elektronik Gmbh Differenzdruckschalter
DE19915319C2 (de) * 1998-09-02 2002-06-13 Eckerle Ind Elektronik Gmbh Doppel-Zahnradpumpe
CN102439306B (zh) * 2009-04-02 2014-12-10 胡斯可国际股份有限公司 具有由电动液压阀联接于分开的外部端口的气缸的流体工作机

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1192104A (fr) * 1951-08-30 1959-10-23 Pompe hydraulique à excentrique
US3000319A (en) * 1957-08-07 1961-09-19 Gen Motors Corp Pump control
US3682565A (en) * 1970-08-31 1972-08-08 Donald L Yarger Multiple piston pump apparatus
FR2292854A1 (fr) * 1974-11-29 1976-06-25 Rexroth Sigma Perfectionnements apportes aux machines a fluide a pistons radiaux

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB457966A (en) * 1935-08-08 1936-12-09 Bosch Robert Improvements in or relating to double-acting single piston pumps
US2450248A (en) * 1944-10-07 1948-09-28 Cities Service Oil Co Grease dispensing unit
US2820415A (en) * 1956-03-12 1958-01-21 Ray W Born Low pressure, high volume-high pressure, low volume pump
US2948222A (en) * 1958-08-04 1960-08-09 William S Pine Pump
DE1453478A1 (de) * 1962-11-16 1969-02-13 Deere & Co Ventil zum selbsttaetigen Regeln von Kolbenpumpen,insbesondere Radialkolbenpumpen
US3776665A (en) * 1971-07-08 1973-12-04 Westran Corp Two stage fluid pump
DE2622010C3 (de) * 1976-05-18 1982-04-01 G.L. Rexroth Gmbh, 8770 Lohr Hydrostatische Radialkolbenpumpe
DE2716888C3 (de) * 1977-04-16 1985-08-22 Mannesmann Rexroth GmbH, 8770 Lohr Hydrostatische Radialkolbenpumpe

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1192104A (fr) * 1951-08-30 1959-10-23 Pompe hydraulique à excentrique
US3000319A (en) * 1957-08-07 1961-09-19 Gen Motors Corp Pump control
US3682565A (en) * 1970-08-31 1972-08-08 Donald L Yarger Multiple piston pump apparatus
FR2292854A1 (fr) * 1974-11-29 1976-06-25 Rexroth Sigma Perfectionnements apportes aux machines a fluide a pistons radiaux

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0428374A1 (fr) * 1989-11-13 1991-05-22 Hobourn Automotive Limited Systèmes de pompe à déplacement positif

Also Published As

Publication number Publication date
JPS54141405A (en) 1979-11-02
DE2817173A1 (de) 1979-10-25
EP0005190B1 (fr) 1981-12-02
ATA233779A (de) 1980-07-15
AT361301B (de) 1981-03-10
US4257750A (en) 1981-03-24

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