EP1090229B1 - Systeme de commande pour equipement hydraulique - Google Patents

Systeme de commande pour equipement hydraulique Download PDF

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Publication number
EP1090229B1
EP1090229B1 EP99920454A EP99920454A EP1090229B1 EP 1090229 B1 EP1090229 B1 EP 1090229B1 EP 99920454 A EP99920454 A EP 99920454A EP 99920454 A EP99920454 A EP 99920454A EP 1090229 B1 EP1090229 B1 EP 1090229B1
Authority
EP
European Patent Office
Prior art keywords
pump
adjusting element
piston pump
radial piston
radial
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.)
Expired - Lifetime
Application number
EP99920454A
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German (de)
English (en)
Other versions
EP1090229A1 (fr
Inventor
Johann Auer
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.)
Weber Hydraulik GmbH Austria
Original Assignee
Weber Hydraulik GmbH Austria
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Filing date
Publication date
Application filed by Weber Hydraulik GmbH Austria filed Critical Weber Hydraulik GmbH Austria
Publication of EP1090229A1 publication Critical patent/EP1090229A1/fr
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Publication of EP1090229B1 publication Critical patent/EP1090229B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • 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
    • F04B1/06—Control
    • F04B1/07—Control by varying the relative eccentricity between two members, e.g. a cam and a drive shaft
    • 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
    • F04B49/12—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 varying the length of stroke of the working members
    • F04B49/123—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 varying the length of stroke of the working members by changing the eccentricity of one element relative to another element
    • F04B49/125—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 varying the length of stroke of the working members by changing the eccentricity of one element relative to another element by changing the eccentricity of the actuation means, e.g. cams or cranks, relative to the driving means, e.g. driving shafts

Definitions

  • the invention relates to a radial piston pump with an eccentric adjusting element with several pump pistons driven by a common drive shaft, as described in the preamble of claim 1 (see e.g. US-A-2 709 408).
  • the object of the invention is a pump device of the radial piston pump type to create with an eccentric adjustment element that is largely Self-regulation of the delivery volume depending on the system pressure during the Operation enabled.
  • This object of the invention is achieved by the characterizing part of claim 1 reproduced characteristics achieved.
  • the surprising advantage here is that for Regulation of the pump output for a according to requirements on the delivery volume a mechanically simple pump equipped with any number of pumping elements and thus reliable, between the drive device and the pump device arranged control system is achieved, the configurations for self-regulation allows at the predetermined regardless of consumers used Working speeds can be achieved.
  • An embodiment according to claim 3, which optimizes the adjustment path, is also advantageous enables, thereby minimizing the dimensions of such pumping devices become.
  • Claim 7 describes an advantageous embodiment whereby the rotational movement of the Drive shaft is transferred to the adjusting element via the insert spring without play, without restricting the axial mobility of the adjusting element on the drive shaft.
  • the Installation work kept to a minimum by eliminating pipelines and malfunctions through leaks, such as with screw connections and pipes due to vibration loads avoided.
  • a training according to claims 16 and 17 is also advantageous, with a use of an adjusting element with a differently designed adjusting eccentric or a sliding surface that runs at a different angle is that the piston shoes can move on all sides and so everyone Can adjust angles.
  • Claims 18 to 25 describe a possible further development external control and control device saved, because by supporting the Pump piston on the angular sliding surface by the pressure force, which the pump pistons apply via the piston shoes a reaction force in axial direction of the drive shaft, which is the spring force of the return springs Counteracting adjustment.
  • the pressure force of the return springs is considered matched to the reaction force, which results in a predetermined maximum pressure level can be realized with automatic control. This enables a very simple one mechanical structure of the entire pumping device.
  • a radial piston pump 1 is shown, which consists of a pump device 2 and a drive device 3 is formed.
  • the drive device 3 In this example comprises a motor 4 which is controlled via a control device 5 becomes.
  • the radial piston pump 1 is on a base plate 6 or a tubular frame etc. stored, which are preferably vibration-damping feet 7th is supported on a contact surface 8.
  • the pump device 2 is in a storage container 9 arranged and constantly surrounded by medium 10 located in the reservoir 9.
  • This medium 10 is preferably a print medium, such as e.g. Hydraulic oil.
  • the reservoir 9 is for filling with the medium 10 with an inlet opening 11 provided, and the closure device with a known level indicator 12 provided, via which a control of the level of the reservoir 9 allows becomes.
  • the closure device with a known level indicator 12 provided, via which a control of the level of the reservoir 9 allows becomes.
  • At the lowest point of the storage container 9 is one with a screw 13 closed outlet opening 14 is arranged, via which an emptying of the storage container 9, e.g. for the periodic exchange of the Medium 10 takes place.
  • the storage container 9 is preferably formed from folded sheet metal and is over an all-round flange 15 is attached to a housing part 16, e.g. screwed to this, here any other possible, sealing closure guaranteeing attachment type can be used.
  • the housing part 16 is connected to a flange plate 17, which is opposite the housing part 16 is designed to receive the drive device 3, e.g. with centering attachment for the central mounting of the motor 4.
  • the pump device 2 in turn is now activated by a drive device 3 or the motor 4 protruding drive shaft 18 and one on this in the axial Direction slidable adjusting element 19 formed with on the housing part 16 arranged pump elements 20 cooperates.
  • the pump elements 20 are standard conveying elements for a medium 10, such as Hydraulic oil, and as such are of the self-priming type.
  • a medium 10 such as Hydraulic oil
  • a pump housing 21 is in a bore 22 an adjustable against the action of a spring 23 pump piston 24 arranged.
  • the pump piston 24 points out of the pump housing 21 outstanding end area on a so-called piston shoe 25, which by the Effect of the spring 23 or by the medium 10 applied to the pump piston 24 Force is brought to bear on the adjusting element 19.
  • the adjustment element 19 is shown in FIG Axial direction of the drive shaft 18, an actuator 26 is provided by a external pressure generator is fed and which an adjustment of the adjusting element 19 along the drive shaft 18 and by means of one from the outside Determinable volume and pressure characteristics of the pump device 2 is achieved.
  • the pump elements 20 are self-priming when a negative pressure occurs in the bore 22, the medium 10 via a backflow blocking inlet openings suck in and by means of pump outputs 27 when adjusting the pump piston 24 of the adjusting element 19 under pressure build-up.
  • the pump outputs 27 of the Pump elements 20 are now connected to one another and arranged in the housing part 16 Bores 28 line-connected, which creates a common pressure build-up is made possible via all pump elements 20. Through this training that all Pump outputs 27 are connected to one another via the bores 28 enables the medium 10 at an outlet 29 with a relatively constant pressure to deliver and to a consumer, e.g. a hydraulically operated tool.
  • the adjusting element 19 is now shown in section in a side view.
  • the adjusting element 19 has a receiving bore 30 for receiving the drive shaft 18 of the drive device 3.
  • the receiving bore 30 and the drive shaft 18 of the drive device 3 have a common central axis 31, which extends over the entire length of the adjusting element 19 and thus a rotation the same around the central axis 31 allows.
  • the adjustment element 19 forms an adjustment eccentric 33, which by a oblique cylinder body 34 is formed, with a central axis 35 of the cylinder body 34 extends at an acute angle to the central axis 31 of the drive shaft 18.
  • the adjusting eccentric 33 or the cylinder body 34 is formed by a lateral surface 36 a sliding surface 37 for the pump piston 24. This means that the central axis 35 of the circumferential sliding surface 37 of the adjusting eccentric 33 angled, in particular at an acute angle 38 to the central axis 31 of the drive shaft 18 or the adjusting element 19 receiving the adjusting eccentric 33 is.
  • the adjusting element 19 also has a parallel to its central axis 31 Receiving holes 39, which for receiving any restoring elements for the Adjustment eccentric 33 or the adjustment element 19 can be formed.
  • a parallel length 40 of the adjusting eccentric measured to the central axis 31 of the adjusting element 19 33 is essentially less than an overall length 41 of the adjusting element 19.
  • a recess 42 or a bore 43 is provided for receiving an axial bearing.
  • This bore 43 has a smaller diameter 44 than the receiving bore 30 on, whereby a complete penetration of the drive shaft 18 through the Adjustment element is not possible.
  • the angle 38 which is from the central axis 31 of the drive shaft 18 and the central axis 35 of the adjusting eccentric 33 or of the cylinder body 34 is enclosed, is freely chosen according to the desired adjustment characteristic, but is approximately be between 5 ° and 15 °.
  • Actuator 26 for adjusting the adjusting element 19 is on the housing part 16 fastens a housing 50, which coaxially surrounds the adjusting element 19, which is provided with openings so that the adjusting element 19 as a whole runs in an oil bath formed by the medium 10.
  • an axial displacement of the adjusting eccentric 33 Enabling adjusting element 19 is in one of the drive means 3 facing end region 51 of the housing 50 of the actuator 26, which is operated via an external pressure system or by any other type of drive can be driven.
  • the actuator 26 now has one via a connector 52 and a supply line 53 pressurized pressure piston 54, with a central axis 55 of the pressure piston 54 along a central axis of the adjusting element 19 or a central axis 31 of the drive shaft 18.
  • This pressure piston 54 is before the housing 50 is mounted on the housing part 16 via a threaded piece 56, in which the pressure piston 54 is mounted in a sliding fit, brought in.
  • the threaded piece 56 is a circumferential in the direction of the connector 52 Seal 57 assigned to a passage of a pressure fluid through the Avoid threaded piece 56, which ensures proper functioning of the pressure piston 54 could be affected.
  • This pressure piece 58 On the end region of the pressure piston 54 facing the adjusting element 19 a pressure piece 58 attached.
  • This pressure piece 58 has an approximately T-shaped Cross section and lies with an end face 59 assigned to the pressure piston 54 on an inner surface 60 of the housing 50 when the pressure piston is in a pressure-free state 54, the pressure piece 58 of the adjusting element 19 on its housing side End area is assigned.
  • An extension 61 of the pressure piston 54 extending along the central axis 55 has a diameter 62, which is preferably less than the diameter 44 of the bore 43 in the adjusting element 19.
  • an axial bearing 64 is now arranged or fastened by which an unimpeded rotational movement of the adjusting element 19 even when brought up Pressure piston 54 to the adjusting element 19 is guaranteed.
  • In the thigh 63 is arranged at least one guide pin 65 held in this by a press fit, which extends in the direction of the connector 52.
  • This guide pin 65 is in a bore 66, which is carried out in the housing 50, in the axial Slidably supported in the direction.
  • An anti-rotation device is provided by the guide pin 65 reached for the pressure piece 58 attached to the pressure piston 54, which under Interposition of the axial bearing 64 an actuating force on the with the drive shaft 18th co-rotating adjustment element 19 exercises.
  • the receiving bores are now in the adjusting element 19 or in the adjusting eccentric 33 39 arranged, these receiving bores 39 central axes 67, which run parallel to the central axis 55.
  • These receiving holes 39 are designed to receive return springs 68 which are against a support device Support 69, the axial force against a bearing arrangement accommodates the housing part 16.
  • a length of the return springs 68 or the receiving bores 39 can be selected in various ways, but the restoring forces must be distributed all around such that they move the adjusting element 19 in parallel ensure to the central axis 31 of the drive shaft 18.
  • the pump elements 20 are now star-shaped and at a distance 70 from the central axis 31 the drive shaft 18 arranged on the housing part 16, these pump elements 20 which have pump pistons 24 running perpendicular to the central axis 31.
  • the adjusting eccentric 33 By designing the adjusting eccentric 33 as an oblique cylinder body 34 or due to the angular course of the sliding surface 37 relative to the central axis 31 reaches an inclined position of the piston shoes 71, as a result of which they have an axial reaction force exert on the adjustment eccentric 33. It also acts on the pressure piston 54 the pressure generated by the system itself, or an external control pressure. From the Surface of the pressure piston 54 results in a force that sums with the reaction force from the inclined position of the piston shoes 71 against the adjustment eccentric The spring forces of the return springs 68 are shifted until the forces are balanced prevails.
  • the axial force for adjusting the adjusting eccentric 33 can be increased be by the pressure piston 54 via the connector 52 or the supply line 53 with a higher external control pressure, whereby another Displacement of the adjusting element 19 along the central axis 31 is made possible.
  • the pressure piece 58 has an actuator 26 for the adjusting element 19 is assigned to overcome the restoring force of the restoring springs 68, the actuator 26 being axially adjustable in the threaded piece 56 Pressure piston 54 is formed.
  • the adjusting eccentric 33 has a lifting height 72, which by an axial displacement of the adjusting element 19 or the adjusting eccentric 33 freely can be chosen.
  • This stroke height 72 corresponds to a piston path 73 of the pump piston 24, which in turn makes the dependence of the eccentricity of the adjusting eccentric 33 and the stroke height 72 of the pump piston 24 are illustrated from one another.
  • the central axis 35 runs as an oblique cylinder body 34 trained adjusting eccentric 33 at an acute angle 38 and cuts in a zero point 74, the central axis 31 of the drive shaft 18 and the adjusting element 19.
  • the illustration in FIG. 4 illustrates the maximum delivery rate of the pump elements 20.
  • By moving the adjusting element 19 in the direction of the drive unit 3 takes the eccentricity of the oblique cylinder body 34 compared to the Center axis 31 from.
  • the piston path 73 of the pump piston 24 is also reduced their piston shoes 71 along their central axis 75, and there is a reduction the flow rate.
  • the adjustment element 19 can move along the maximum adjustment path 76 its central axis 31 are shifted, which is the constructively wanted minimal flow rate results.
  • an adjustment path 76 is chosen so large that the central axis 75 of the pump piston 24 with the Intersection 74 of the central axes 31 and 35 is congruent. In this position shows the radial piston pump 1 when the adjusting element 19 or the adjusting eccentric rotates 33 no delivery rate.
  • the support device 69 is formed all around, so that they in the case of a rotational movement of the adjusting element 19 passes through the same movement, and so takes over the support of the return springs 68.
  • the support device 69 serves as a limitation of the adjustment path 76 educated.
  • these return springs 68 are the adjusting element Stabilize 19 in its position shown in Fig. 4, and that in the case an axial displacement of the adjusting element 19 in the direction of the drive device 3, the holding force of these return springs 68 via the pressure piece 58 or via the pressure-operated pressure piston 54 must be overcome.
  • 5 and 6 is a further embodiment of a pump device according to the invention 2 shown.
  • Adjustment element 19 with the adjustment eccentric 33 axially along the one above the other Central axes 31 of the adjusting element 19 or the drive shaft 18 are displaceable is mounted on the drive shaft 18.
  • This insert spring 47 is used purely for transmitting the rotary movement the drive shaft 18 on the adjusting element 19 and leaves an axial displacement of the adjusting eccentric 33 having the adjusting element 18 in the axial direction Direction along the central axis 31 to.
  • the return springs 68 are supported by internal bolts 80, which results in a Deformation or buckling of the return spring 68 avoided under high loads shall be.
  • an insert 81 is arranged on the drive shaft 18, which has a rotating Forms flange and an end stop for the axial displacement of the adjusting element 19 results in its position remote from the drive device 3.
  • a Base 82 of stop device 81 projects into receiving bore 30 of the adjusting element 19 and comes with an end face facing the drive shaft 18 83 on the end face 48 of the same.
  • a circumferential leg 84 of the stop device 81 has a larger diameter 85 than the through hole 30 of the adjusting element 19. This training enables the circumferential leg 84 of the stop device 81 on an end face 86 of the Adjusting element 19 abuts and so the adjusting element 19 in its by the return springs 68 position taken fixed.
  • the stop device 81 has one Through hole 87 through which a screw 88 is passed and so attachment of the stop device 81 is made possible.
  • a blind hole 89 through which screwing in the screw 88 is made possible, thereby fastening the stop device 81 is realized on the drive shaft 18.
  • the Stop device 81 a safeguard against axial displacement of the insert spring 47, whereby a rotationally fixed arrangement of the adjusting element 19 on the drive shaft 18 is ensured.
  • the desired axial adjustment of the adjusting element 19 by the force of the pump piston 24 or the piston shoes 71 he follows. Via the pump elements 20 arranged radially around the adjusting element 19 a certain delivery rate is reached, gradually increasing the working pressure builds up in the printing system or in the consumer. Now increases the required in the printing system Working pressure, the pressure on the pump piston 24 is increased. This Pressure is now on the piston shoes 71 on the adjusting element 19 or Adjusting eccentric 33 or on its angled to the central axis 31 of the adjusting element 19 extending sliding surface 37, whereby a perpendicular to the sliding surface 37 acting pressure force 90 results. This pressure force 90 is now broken down a parallelogram of forces into a radially acting force component 91 and into one axially acting force component 92.
  • the adjustment of the adjusting element 19 is in the axial direction in the case when the axially acting force component 92 opposes it acting restoring force of the return spring 68 exceeds.
  • the piston path 73 is now reduced, as a result of which the delivery rate of the Radial piston pump 1 or the pump elements 20 is reduced.
  • a particular advantage of this training is that the stepless Displacement of the adjusting element 19, the delivery volume to the respective requirements can be adjusted and thus a relatively evenly falling or increasing Performance curve of the radial piston pump 1 is achieved. Furthermore, by adjusting the spring force for the return spring 68 different pressure ranges for radial piston pumps 1.
  • the pressure force 90 acts perpendicular to the angular sliding surface and from it an axially force element 92 acting on adjusting element 19 or adjusting eccentric 33 results, with an increase in the system pressure resulting in the pump pistons 24 acting pressure force 90 and thus the axially acting force component 92 in Dependency of the funding volume increased. Furthermore, if the counteracting restoring force of the return spring 68 by the axially acting Force component initiated the adjustment of the adjusting element 19, wherein through this adjustment of the adjusting element 19, the piston path 73, the pump piston 24 of the pumping elements 20 is reduced via the adjusting eccentric 33 and so that Delivery volume of the radial piston pump 1 is also reduced.
  • FIGS. 1, 2; 3; 4; 5, 6 shown versions form the subject of independent solutions according to the invention.
  • the related Tasks and solutions according to the invention are the detailed descriptions these figures.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)

Claims (28)

  1. Pompe à pistons radiaux avec une partie de boítier (16) en forme de plaque, présentant des perçages pour le convoyage d'un milieu et de préférence avec une installation d'entraínement (3) fixée à la partie de boítier (16) et avec un réservoir (9) disposé en face de l'installation d'entraínement (3) d'une manière étanche au liquide à la partie de boítier (16) pour le milieu et un excentrique d'ajustement (33) disposé dans celui-ci pour des éléments de pompe (20) disposés dans la direction périphérique de celui-ci à la partie de boítier (16), qui comportent des pistons de pompe (24), pouvant être chargés par un élément d'ajustement (19) de l'excentrique d'ajustement (33), déplaçables dans la direction radiale, caractérisée en ce que l'élément d'ajustement (19) reçoit dans un perçage de réception (30) un arbre d'entraínement (18) de l'installation d'entraínement (3) traversant la partie de boítier (16) et est logé sur l'arbre d'entraínement (18) d'une manière immobile en rotation et déplaçable dans la direction axiale et est formé par un corps cylindrique biais (34) qui réalise avec une face d'enveloppe (36) une face de glissement (37) pour les pistons de pompe (24).
  2. Pompe à pistons radiaux selon la revendication 1, caractérisée en ce qu'un axe médian (35) du corps cylindrique (34) s'étend selon un angle à un axe médian (31) du perçage de réception (30) respectivement de l'arbre d'entraínement (18).
  3. Pompe à pistons radiaux selon la revendication 1 ou 2, caractérisée en ce que la face d'enveloppe (36) est formée par la surface d'un corps conique, et en ce qu'un axe médian longitudinal du corps conique s'étend selon un angle à l'axe médian du perçage de réception (39) respectivement de l'arbre d'entraínement (18).
  4. Pompe à pistons radiaux selon l'une ou plusieurs des revendications précédentes, caractérisée en ce que l'élément d'ajustement (19) peut être positionné par des ressorts de rappel (68) réalisant un dispositif à ressorts, disposé à peu près parallèlement à l'arbre d'entraínement (18) dans des perçages de réception (30), dans une position d'extrémité espacée de la partie de boítier contre un dispositif de butée (81) et/ou une pièce de pression (58) d'une commande de positionnement (26).
  5. Pompe à pistons radiaux selon l'une ou plusieurs des revendications précédentes, caractérisée en ce que les ressorts de rappel (68) prennent appui dans leur zone d'extrémité opposée à l'élément d'ajustement (19) sur un dispositif d'appui annulaire (69).
  6. Pompe à pistons radiaux selon l'une ou plusieurs des revendications précédentes, caractérisée en ce que le dispositif d'appui (69) entoure annulairement un prolongement cylindrique de l'élément d'ajustement (19) et s'appuie dans la direction axiale sur une bague intérieure d'un palier radial (77) disposé dans la partie de boítier (16), logeant l'élément d'ajustement (19).
  7. Pompe à pistons radiaux selon l'une ou plusieurs des revendications précédentes, caractérisée en ce que l'élément d'ajustement (19) est couplé d'une manière immobile en rotation par un ressort d'insertion (47) à l'arbre d'entraínement (18).
  8. Pompe à pistons radiaux selon l'une ou plusieurs des revendications précédentes, caractérisée en ce qu'il est disposé dans un boítier (50) entourant l'élément d'ajustement (19) au côté de la périphérique et au côté frontal une commande de positionnement (26) pour l'élément d'ajustement (19).
  9. Pompe à pistons radiaux selon l'une ou plusieurs des revendications précédentes, caractérisée en ce qu'il est disposé entre la pièce de pression (58) de la commande de positionnement (26) et une face frontale dans un évidement (42) de l'élément d'ajustement (19) un palier axial (64).
  10. Pompe à pistons radiaux selon l'une ou plusieurs des revendications précédentes, caractérisée en ce que la commande de positionnement (26) exerce avec la pièce de pression (58) par un piston de compression (54) chargé en un milieu sous pression une force de déplacement sur l'élément d'ajustement (19) contre l'effet des ressorts de rappel (68).
  11. Pompe à pistons radiaux selon l'une ou plusieurs des revendications précédentes, caractérisée en ce que la pièce de pression (58) est logée d'une manière assurée à l'encontre d'une rotation par au moins une tige de guidage s'engageant dans un perçage dans le carter de pompe (21) le long de l'axe médian (31) de l'arbre d'entraínement (18) d'une manière ajustable dans le carter de pompe (21).
  12. Pompe à pistons radiaux selon l'une ou plusieurs des revendications précédentes, caractérisée en ce qu'il est logé dans la pièce de pression (58) le piston de compression (54) d'une manière immobile en déplacement par un ajustement serré.
  13. Pompe à pistons radiaux selon l'une ou plusieurs des revendications précédentes, caractérisée en ce que le piston de compression (54) est en liaison avec une commande de moyen de pression qui est réalisée en vue du déplacement axial du piston de compression (54).
  14. Pompe à pistons radiaux selon l'une ou plusieurs des revendications précédentes, caractérisée en ce que des perçages (28), en tant que conduits de pression des éléments de pompe (20) sont reliés d'une manière communicante dans la partie de boítier (16).
  15. Pompe à pistons radiaux selon l'une ou plusieurs des revendications précédentes, caractérisée en ce que la plaque de bride (17) portant la partie de boítier (16) respectivement le carter de pompe (21) est fixée sur l'installation d'entraínement (3), de préférence est assemblée par vissage avec celle-ci.
  16. Pompe à pistons radiaux selon l'une ou plusieurs des revendications précédentes, caractérisée en ce que sont disposés aux pistons de pompe (24) des sabots de piston (71) reliés à ceux-ci et s'appuyant sur la face de glissement (37) de l'excentrique d'ajustement (33).
  17. Pompe à pistons radiaux selon l'une ou plusieurs des revendications précédentes, caractérisée en ce que les sabots de piston (71) sont disposés d'une manière pivotante de tout côté sur les pistons de pompe (24).
  18. Pompe à pistons radiaux selon l'une ou plusieurs des revendications précédentes, caractérisée en ce qu'un déplacement axial de l'élément d'ajustement (19) a lieu sous un effet de forces des pistons de pompe (24) respectivement des sabots de piston (71) en fonction de la pression du système.
  19. Pompe à pistons radiaux selon l'une ou plusieurs des revendications précédentes, caractérisée en ce que l'élément d'ajustement (19) est déplaçable par le chemin de déplacement (76) entre une position où la face de glissement (37) pour les pistons de pompe (24) présente une excentricité zéro, et une position dans laquelle l'excentricité atteint la valeur maximale.
  20. Pompe à pistons radiaux selon l'une ou plusieurs des revendications précédentes, caractérisée en ce que l'effet de force est exercé perpendiculairement à la face de glissement (37) s'étendant d'une manière angulaire et qu'il en résulte une composante de force (91, 92) agissant axialement sur l'élément d'ajustement (19) respectivement l'excentrique d'ajustement (33).
  21. Pompe à pistons radiaux selon l'une ou plusieurs des revendications précédentes, caractérisée en ce que par suite d'une augmentation de la pression du système, la composante de force (92) agissant axialement des éléments de pompe (20) augmente.
  22. Pompe à pistons radiaux selon l'une ou plusieurs des revendications précédentes, caractérisée en ce que lors d'un dépassement de la force de rappel agissant d'une manière opposée par la composante de force agissant axialement (92), le déplacement de l'élément d'ajustement (19) est introduit.
  23. Pompe à pistons radiaux selon l'une ou plusieurs des revendications précédentes, caractérisée en ce que par le déplacement de l'élément d'ajustement (19), le chemin de piston (73) des pistons de pompe (24) des éléments de pompe (20) est diminué par l'excentrique d'ajustement (33) et ainsi le volume convoyé par la pompe à pistons radiaux (1) est diminué.
  24. Pompe à pistons radiaux selon l'une ou plusieurs des revendications précédentes, caractérisée en ce que le déplacement de l'élément d'ajustement (19) est effectué jusqu'à l'atteinte d'un équilibre entre la force de rappel et la composante de force (92) agissant axialement.
  25. Pompe à pistons radiaux selon l'une ou plusieurs des revendications précédentes, caractérisée en ce qu'il est obtenu par le réglage progressif de l'élément d'ajustement (19) par l'excentrique d'ajustement (33) une quantité convoyée augmentant ou diminuant régulièrement.
  26. Pompe à pistons radiaux selon l'une ou plusieurs des revendications précédentes, caractérisée en ce qu'un angle (38) entre l'axe médian (31) et l'axe médian (35) représente environ entre 5° et 15° et qu'il est de préférence de 10°.
  27. Pompe à pistons radiaux selon l'une ou plusieurs des revendications précédentes, caractérisée en ce qu'un chemin de déplacement (76) de l'élément d'ajustement (19) est compris entre 8 mm et 30 mm, et qu'il est de préférence de 15 mm.
  28. Pompe à pistons radiaux selon l'une ou plusieurs des revendications précédentes, caractérisée en ce qu'une excentricité maximale de la face de glissement (37) s'étendant angulairement à l'axe médian (31) est approximativement de 6 mm.
EP99920454A 1998-05-22 1999-05-18 Systeme de commande pour equipement hydraulique Expired - Lifetime EP1090229B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
AT0033898U AT3212U1 (de) 1998-05-22 1998-05-22 Radialkolbenpumpe
AT33898U 1998-05-22
PCT/AT1999/000125 WO1999061797A1 (fr) 1998-05-22 1999-05-18 Systeme de commande pour equipement hydraulique

Publications (2)

Publication Number Publication Date
EP1090229A1 EP1090229A1 (fr) 2001-04-11
EP1090229B1 true EP1090229B1 (fr) 2003-03-26

Family

ID=3487949

Family Applications (1)

Application Number Title Priority Date Filing Date
EP99920454A Expired - Lifetime EP1090229B1 (fr) 1998-05-22 1999-05-18 Systeme de commande pour equipement hydraulique

Country Status (6)

Country Link
US (1) US6478548B1 (fr)
EP (1) EP1090229B1 (fr)
AT (2) AT3212U1 (fr)
AU (1) AU3803099A (fr)
DE (1) DE59904744D1 (fr)
WO (1) WO1999061797A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2006544A2 (fr) 2007-06-18 2008-12-24 Weber-Hydraulik GmbH Pompe à pistons avec excentricité variable
US9194380B2 (en) 2011-10-21 2015-11-24 Hydr'am Radial hydraulic pump with a variable eccentricity and delivery

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN106069876A (zh) * 2016-08-08 2016-11-09 广东南牧机械设备有限公司 控料器
DE102017206723A1 (de) * 2017-04-21 2018-10-25 Mando Corporation Kolbenpumpenanordnung umfassend einen Kolben mit variablem Hub
DE102020114915B4 (de) * 2020-06-04 2022-04-21 Reichhardt Gmbh Steuerungstechnik Vorrichtung zum Lagern eines ein Aushebewerkzeug bewegenden Tragarms an einer Erntemaschine
CN113229974B (zh) * 2021-04-30 2022-09-30 深圳素士科技股份有限公司 泵壳、泵组件及口腔护理装置

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DE543934C (de) 1930-05-10 1932-02-11 August Rinderknecht Kolbenpumpe
FR841996A (fr) 1938-08-11 1939-06-02 Dispositif hydraulique pour la transmission d'un mouvement à différentes vitesses
US2356993A (en) 1943-02-04 1944-08-29 Midwest Hydraulics Inc Radial pump
US2539277A (en) 1945-03-09 1951-01-23 Martin A High Variable stroke pump
US2612837A (en) 1946-05-21 1952-10-07 American Eng Co Ltd Pump
FR930884A (fr) 1946-07-20 1948-02-06 Pompe hydraulique à volume variable
US2709408A (en) 1951-01-25 1955-05-31 Ibm Variable displacement radial piston pump
DE1112431B (de) 1958-02-12 1961-08-03 Erich Baentsch Pumpe einer Spritzeinrichtung fuer fluessiges UEberzugsgut
GB1149273A (en) 1966-06-23 1969-04-23 Nippon Kikai Keiso Kaisha Ltd Variable-stroke reciprocating pumps
US3492948A (en) 1968-04-08 1970-02-03 Haviland H Platt Hydraulic pump/motor
US3906842A (en) * 1972-01-31 1975-09-23 Iwaki Co Ltd Variable metering pump
US3827831A (en) * 1972-05-15 1974-08-06 R Lines Control for radial type pumps or the like
US3924490A (en) * 1974-05-21 1975-12-09 Ned D Mills Variable ratio drive unit and method
US4041800A (en) 1975-04-07 1977-08-16 Nikkiso Co., Ltd. Stroke length adjusting devices
FR2321608A1 (fr) 1975-08-20 1977-03-18 Bechler Andre Pompe hydraulique a debit reglable en continu
US4261228A (en) 1978-12-13 1981-04-14 Eagan Joseph A Sen Stroke adjustment for reciprocating mechanism
EP0099000B1 (fr) * 1982-07-15 1988-12-07 WAP-Reinigungssysteme GmbH & Co. Machine à piston ayant des cylindres en étoile
US4768422A (en) * 1986-09-15 1988-09-06 Swinney Louis E Pump motor
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JPH04347380A (ja) * 1991-05-22 1992-12-02 Honda Motor Co Ltd 圧縮比調整機構付きラジアルプランジャ装置
DE4122486A1 (de) * 1991-07-06 1993-01-07 Teves Gmbh Alfred Antriebsaggregat, insbesondere motor-pumpenaggregat fuer schlupfgeregelte bremsanlagen
DE4132456A1 (de) 1991-09-30 1993-04-01 Bosch Gmbh Robert Radialkolbenmaschine
US5368448A (en) * 1992-02-27 1994-11-29 Honda Giken Kogyo Kabushiki Kaisha Variable-stroke crank mechanism
WO1999061796A1 (fr) * 1998-05-26 1999-12-02 Caterpillar Inc. Systeme hydraulique avec pompe a debit variable

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2006544A2 (fr) 2007-06-18 2008-12-24 Weber-Hydraulik GmbH Pompe à pistons avec excentricité variable
US9194380B2 (en) 2011-10-21 2015-11-24 Hydr'am Radial hydraulic pump with a variable eccentricity and delivery

Also Published As

Publication number Publication date
US6478548B1 (en) 2002-11-12
AT3212U1 (de) 1999-11-25
ATE235657T1 (de) 2003-04-15
WO1999061797A1 (fr) 1999-12-02
EP1090229A1 (fr) 2001-04-11
AU3803099A (en) 1999-12-13
DE59904744D1 (de) 2003-04-30

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