EP0884476B1 - Circuit de contrôle de pression de sécurité pour une pompe hydraulique radiale ou axiale à cylindrée variable ou une machine à cellules semi-rotatives - Google Patents

Circuit de contrôle de pression de sécurité pour une pompe hydraulique radiale ou axiale à cylindrée variable ou une machine à cellules semi-rotatives Download PDF

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Publication number
EP0884476B1
EP0884476B1 EP98105057A EP98105057A EP0884476B1 EP 0884476 B1 EP0884476 B1 EP 0884476B1 EP 98105057 A EP98105057 A EP 98105057A EP 98105057 A EP98105057 A EP 98105057A EP 0884476 B1 EP0884476 B1 EP 0884476B1
Authority
EP
European Patent Office
Prior art keywords
pressure
working machine
valve
machine
adjustable hydraulic
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
EP98105057A
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German (de)
English (en)
Other versions
EP0884476A3 (fr
EP0884476A2 (fr
Inventor
Volkmar Leutner
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.)
Robert Bosch GmbH
Original Assignee
Robert Bosch 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 Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP0884476A2 publication Critical patent/EP0884476A2/fr
Publication of EP0884476A3 publication Critical patent/EP0884476A3/fr
Application granted granted Critical
Publication of EP0884476B1 publication Critical patent/EP0884476B1/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
    • 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
    • F04B49/10—Other safety measures
    • 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
    • F04B49/08—Regulating by delivery pressure
    • 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
    • F04B2205/00—Fluid parameters
    • F04B2205/06—Pressure in a (hydraulic) circuit
    • F04B2205/061—Pressure in a (hydraulic) circuit after a throttle

Definitions

  • the invention is based on an adjustable hydraulic Working machine according to the preamble of claim 1 out.
  • a machine in the form of a Radial piston pump is for example from DE-A-3 140 397 or DE 44 10 719.6 A1 is already known.
  • This radial piston pump is equipped with a number of sensors whose signals evaluated in a control unit and to a control signal be processed for an adjustment device that on the Radial piston pump lifting device acts. Aim this The arrangement is to run as quietly as possible To reach radial piston pump. If there is one Mishandling of the adjustment device, the Radial piston pump set to maximum flow become. In extreme cases, i.e. if the pressure supply of the Adjustment device not via the pump outlet but via If an external device is used, this can be done for vacuuming of the connected hydraulic system and then through Lack of lubricant to self-destruct the Guide the radial piston pump.
  • the work machine according to the invention has the characterizing features of claim 1 the advantage a switchable hydraulic safety device on the machine in the event of a fault in emergency operation switches.
  • the Machine regulated to a constant operating pressure, in which the self-destruction of the work machine is excluded.
  • the safety device can be opened relatively simple way in the control valve Integrate adjustment device and is proportionate simple and therefore inexpensive hydraulic components built up. The required components enlarge it Construction volume of the control valve is at most insignificant. Further advantages or advantageous developments of Invention result from the dependent claims or the Description.
  • Figure 1 shows a control loop for adjustment a work machine in a schematic representation, being a single-acting 4/4 proportional control valve used and developed according to the invention.
  • figure 2 is a control loop with a double acting control valve shown.
  • Figure 3 shows the control characteristic of the Control loop according to Figure 2 using a Pressure curve diagram.
  • FIG. 1 In Figure 1 with 10 is shown schematically electrohydraulic control circuit of a conventional Designated work machine 11.
  • the well-known Working machine 11 is shown symbolically and points as Lifting device 12 has an indicated lifting ring.
  • the Lifting device 12 is in a manner not shown in the Housing of the working machine 11 and mounted works with one adjustment device from two opposing piston / cylinder units 14.1 and 14.2 together.
  • the piston / cylinder units 14.1 and 14.2 differ in the size of their piston surfaces and are hydraulically loaded.
  • the work machine according to FIG. 1 is as a radial piston machine or as a vane machine drawn, but it is not on these types limited.
  • the invention is also based on Axial piston machines transferable.
  • the invention is also regardless of whether the work machines 11 as pumps or Motors are operated.
  • Main control variable of the control loop 10 shown 1 shows the instantaneous position of the lifting device 12, to detect one of the piston / cylinder units 14.1 / 2 is provided with a displacement sensor 16.
  • the position sensor 16 is a conventionally known component, the a dependent on the position of the lifting device 12 electrical signal 18 generated.
  • This signal 18 is one Amplifier 20 supplied, the signal 18 with a Compare setpoint 22. From the discrepancies between the The amplifier 20 forms the desired value 22 and the signal 18 electrical control signal 24 for a control valve 26.
  • Das Control valve 26 converts the control signal 24 into hydraulic signal for the lifting device 12 of the Working machine 11 um.
  • the control valve 26 is a state of the art Technology essentially known 4/4 proportional control valve, which in a solenoid 28 and a hydraulic part 30 coupled thereto is structured.
  • the housing of the magnetic part 28 is a proportional magnet 32 arranged, the an anchor 34 in a spatial direction applied.
  • the armature 34 actuates one in the housing of the Hydraulic part 30 movably guided valve slide 36.
  • Der Valve slide 36 controls by means of control edges, which are transverse its longitudinal axis are arranged, the pressure medium flow of or to hydraulic channels and hydraulic connections 38, which in the Housing of the hydraulic part 30 are formed. With the Hydraulic connections 38 are connected to the lines various consumers, including to the piston / cylinder units 14.1 / 2 of the adjustment device of the Guide machine 11.
  • Valve spool 36 or the armature 34 is carried out by a Hydraulic part 30 arranged control spring 40.
  • This control spring 40 is based on the side facing away from the anchor 34 Valve spool 36 on this valve spool 36 itself and on Because of a housing-side spring chamber 42.
  • the control valve 26 is located opposite the spring chamber 42 a pressure chamber 44. The two ends of the Valve slide 36 protrude with its end faces in the Spring chamber 42 or into the pressure chamber 44.
  • connection 38.1 forms the inlet P of the control valve 26.
  • the connection 35.2 acts as work port B and is with the Piston cylinder unit 14.1 connected during the connection 38.3 connected as a return T to a reservoir 50 is.
  • the working connection designated 38.4 is in Embodiment is not required and is outward, for example by a plug, not shown locked.
  • Longitudinal channels 46.1 and 2 are formed, which interact allow between the individual connections 38.1 to 4.
  • the known hydraulic part 30 of the control valve 26 modified so that the Longitudinal channel 46.1, which is normally a connection from the Spring chamber 42 to the opposite pressure chamber 44 manufactures, is sealed pressure-tight.
  • This can for example a plug, not shown be used.
  • the control valve 26 Additional channels 48.1 and 2 formed, the spring chamber 42nd or contact the pressure chamber 44 hydraulically.
  • the Spring chamber 42 is connected to the additional channel 48.2 Storage container 50 connected and is thereby aerated, while the pressure chamber 44 with the additional channel 48.1 a pressure medium channel 52 is connected.
  • Position transducer 54 To detect the current position of the armature 34 or the Valve spool 36 is a second on the magnetic part 28 Position transducer 54 attached. This displacement sensor 54 generates in a known manner, a position signal 56, which is also the Amplifier 20 supplied and evaluated by this.
  • the described electro-hydraulic control circuit 10 is completed by a connecting channel 58 which leads from the high pressure side of the working machine 11 to the second piston / cylinder unit 14.2.
  • a control circuit 10 allows the adjustment or control of a work machine 11 according to its operating conditions.
  • practical operation has shown that, in exceptional cases, malfunctions or errors can occur in the electrical part of the control circuit 10, which in extreme cases can lead to a maximum adjustment of the machine 11.
  • the work machine 11 can empty the connected hydraulic circuit and then destroy itself due to a lack of lubricant. Helping access in such a case is only possible by timely interruption of the power supply to the drive motor.
  • the control circuit 10 has a safety device 60 according to the invention, which can be integrated into the hydraulic part 30 of the control valve 26.
  • the safety device 60 is switched on electrically after detection of a fault and sets the working machine 11 into a hydraulically controlled, uncritical operating state.
  • the safety device 60 consists of a Pressure medium channel 52, which is the high pressure side of the Machine 11 in the event of a fault with the reservoir 50 connects.
  • a switching valve 62 is located in the pressure medium channel 52 arranged that a pressure medium flow through the Pressure medium channel 52 only releases in the event of a fault. in the trouble-free operation of the working machine 11 is this Pressure medium flow blocked. Switching the switching valve 62 is caused by an electrical interference signal emitted by the Amplifier 20, for example in the event of an implausibility between the signal 18 and the target value 22 is output. At the same time, the current flow to this interference signal Solenoid coil of the proportional magnet 32 of the control valve 26 interrupted.
  • a pressure divider 64 switched in the pressure medium channel 52 is in series with the switching valve 62 a pressure divider 64 switched.
  • This pressure divider 64 will formed by two throttle devices 66.1 and 2, the first throttle device 66.1 the switching valve 62 is connected upstream. That in the area between the two Throttle devices 66.1 and 2 prevailing pressure level tapped via the additional channel 48.1 and the pressure chamber 44 of the control valve 26 supplied.
  • Valve slide 36 with a hydraulic force in the direction its longitudinal axis is applied.
  • the hydraulic power counteracts the force of the control spring 40 and is in it Size of the pressurized face of the Valve spool 36 determines.
  • the pressure divider 64 the force acts on the valve slide 36 proportional to the system pressure of the working machine 11.
  • this force becomes the valve spool 36 of the control valve 26 pressed towards the control spring 40, causing its Control edges the pressure medium flow from port 38.1 to Change connection 38.2 of hydraulic part 30.
  • the piston / cylinder unit 14.1 increases the pressure level, which a further employment of the lifting device 12 of the Working machine 11 causes.
  • the control loop described is based on each other coordinated dimensioning of the face of the Valve slide 26, the control spring 40 and the Throttle device 66.1 / 2 designed such that the Machine 11 in the event of a fault in an operating state is adjusted by setting a pressure level on your High-pressure side regulates that between the two Throttle devices 66.1 / 2 of the pressure divider 64 prevailing Pressure level corresponds.
  • This will be advantageous Pressure level regulated in the range between 10 and 20 bar.
  • Control valve 26a For some applications it is necessary double acting, i.e. in opposite directions use acting control valves 26a. Such a thing Control valve 26a is shown in Figure 2.
  • the control valve 26a has a double stroke magnet in its magnetic part 28a 70 on by an electronic control unit 72 is controlled.
  • the double stroke magnet 70 works with one Anchor 34 together, the valve spool 36 in Hydraulic part 30 actuated.
  • This valve slide 36 instructs both ends on a control spring 40, each on Valve slide 36 itself and at the base of its spring chamber 42 supported.
  • the valve spool 36 are transverse to it Longitudinal axis extending control edges formed Hydraulic channels and hydraulic connections 38 control the Housing of the hydraulic part 30 are formed.
  • the Hydraulic part 30 of the exemplary embodiment has a total of four Hydraulic connections 38.1 to 4, the inlet 38.1, as Return 38.2 and as working connections 38.3 and 38.4 Act. With regard to the contacting of the connections 38.1 to 4, reference is made to FIG. 1 in order to avoid repetitions. Is also identical to the first embodiment, that the longitudinal channel 46 connecting the spring chambers 42 is closed pressure-tight, and that the spring chambers 42nd are contacted hydraulically via additional channels 48.1 / 2.
  • the Safety device 60a This safety device 60a consists of a pressure medium channel 52a, which on the High pressure side of the work machine 11 begins. The Pressure medium channel 52a is the fault-free operation Work machine 11 shut off by a switching valve 62.
  • the switching valve 62 becomes electrical switched and releases the pressure medium flow.
  • this Switching valve 62 branches the pressure medium channel 52a in two channel branches 74.1 / 2, which are parallel to each other Guide storage container 50.
  • both channel branches 74.1 / 2 is one pressure divider 64.1 / 2 each from two in a row switched throttle devices 66.1 / 2 arranged.
  • the Pressure level in the pressure dividers 74.1 / 2 is tapped and through the additional channels 48.1 / 2 the spring chambers 42 of the Control valve 26a supplied.
  • Throttle device 66.2 has a branch channel 76, which of a pressure relief valve 78 is switched.
  • This Pressure relief valve 78 has a return spring and is controlled by the pressure in the pressure divider 64.2.
  • a safety device 60a designed in this way generates a control characteristic as shown in FIG. 3 is shown.
  • Figure 3 the pressure 80.1 / 2 in the Pressure dividers 64.1 / 2 depending on the system pressure 82 of the Work machine 11 applied.
  • the diagram shows that with increasing system pressure 82 the pressure 80.2 of the pressure divider 64.2 initially rises faster than the pressure 80.1 of the Pressure distributor 64.1. Only after passing through the pressure relief valve 78 ( Figure 2) set Pressure threshold 84, the pressure 80.2 remains in the pressure divider 64.2 at a constant level, while the pressure 80.1 in Pressure divider 64.1 continues to rise unchanged and thus that Pressure divider level exceeds 64.2.
  • the working machine 11 means this control characteristic that the lifting device 12 by the control valve 26a as long is issued as long as the pressure 80.2 in the pressure divider 64.2 is greater than the pressure prevailing in the pressure divider 64.1. If the pressures in the pressure dividers 64 are the same, that remains Issue of lifting device 12 constant while at opposite pressure conditions is withdrawn.
  • the work machine 11 is characterized by this control characteristic In the event of a fault, hydraulically into an operating state adjusted and held in the machine provides a system pressure 82 which is in the range between the 2-bis 3 times the set pressure at the pressure relief valve 78 lies.
  • Deviate invention Of course, changes or additions to the Embodiment possible without the basic idea of Deviate invention.
  • Essential to the invention is that conventionally known electrohydraulic controls for Working machines 11 by relatively easy to manufacture Measures on control valve 26 with safety devices 60 can be equipped with a self-destruction and an unintentional employment on full delivery of the Prevent machine 11 in the event of a fault.
  • the Safety device 60 can be used without the construction volume enlarge into the hydraulic part 30 of the control valve 26 integrate.
  • the safety device 60 is off affordable and maintenance-free hydraulic components built up.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Control Of Positive-Displacement Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)

Claims (7)

  1. Machine de travail (11) hydraulique réglable (pompe ou moteur), comprenant un dispositif de réglage (14.1/2) agissant sur un dispositif de levage (12) et excité par une soupape de régulation électrohydraulique (26) présentant un tiroir de soupape (36),
    caractérisée en ce que
    la soupape de régulation (26) coopère avec un dispositif de sécurité (60) qui, en cas de défaut d'excitation du dispositif de réglage (14.1/2), applique une force hydraulique au tiroir de soupape (36) de telle sorte que la soupape de régulation (26) place le dispositif de réglage (14.1/2) raccordé dans une position et le régule dans celle-ci, dans laquelle la machine de travail (11) génère une pression de système du moins approximativement constante.
  2. Machine de travail (11) hydraulique réglable (pompe ou moteur) selon la revendication 1,
    caractérisée en ce que
    le dispositif de sécurité (60) présente une soupape de commutation (62) et au moins un répartiteur de pression (64) comprenant au moins deux dispositifs d'étranglement (66), et la soupape de commutation (62) et le répartiteur de pression (64) sont accouplés en aval l'un de l'autre dans un canal de fluide sous pression (52) qui relie le côté haute pression de la machine de travail (11) au côté basse pression.
  3. Machine de travail (11) hydraulique réglable (pompe ou moteur) selon l'une quelconque des revendications 1 ou 2,
    caractérisée en ce que
    le dispositif de sécurité (60) est intégré dans le carter de la soupape de régulation (26).
  4. Machine de travail (11) hydraulique réglable (pompe ou moteur) selon l'une quelconque des revendications 1 à 3,
    caractérisée en ce que
    dans la soupape de régulation (11) des chambres (42, 44) sont prévues dans lesquelles le tiroir de soupape (36) saillit par les surfaces frontales de ses extrémités, ces chambres (42, 44) sont hydrauliquement découplées l'une de l'autre, et en cas de défaut au moins l'une des chambres (42, 44) est remplie de fluide sous pression.
  5. Machine de travail (11) hydraulique réglable (pompe ou moteur) selon la revendication 4,
    caractérisée en ce que
    le fluide sous pression remplissant au moins l'une des chambres (42, 44) est sous une pression qui correspond à la pression dans le répartiteur de pression (64).
  6. Machine de travail (11) hydraulique réglable (pompe ou moteur) selon l'une quelconque des revendications 1 à 5,
    caractérisée en ce que
    la machine de travail (11) est une machine à pistons, notamment une machine à pistons radiaux ou à pistons axiaux.
  7. Machine de travail (pompe ou moteur) (11) selon l'une quelconque des revendications 1 à 5,
    caractérisée en ce que
    la machine de travail (11) est une machine à cellules semi-rotatives.
EP98105057A 1997-06-12 1998-03-20 Circuit de contrôle de pression de sécurité pour une pompe hydraulique radiale ou axiale à cylindrée variable ou une machine à cellules semi-rotatives Expired - Lifetime EP0884476B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19724870A DE19724870A1 (de) 1997-06-12 1997-06-12 Verstellbare hydraulische Arbeitsmaschine
DE19724870 1997-06-12

Publications (3)

Publication Number Publication Date
EP0884476A2 EP0884476A2 (fr) 1998-12-16
EP0884476A3 EP0884476A3 (fr) 1999-02-03
EP0884476B1 true EP0884476B1 (fr) 2003-10-22

Family

ID=7832281

Family Applications (1)

Application Number Title Priority Date Filing Date
EP98105057A Expired - Lifetime EP0884476B1 (fr) 1997-06-12 1998-03-20 Circuit de contrôle de pression de sécurité pour une pompe hydraulique radiale ou axiale à cylindrée variable ou une machine à cellules semi-rotatives

Country Status (3)

Country Link
EP (1) EP0884476B1 (fr)
JP (1) JPH1150968A (fr)
DE (2) DE19724870A1 (fr)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN100485196C (zh) * 2006-02-11 2009-05-06 中国矿业大学 具有液控或电液控两种工作方式的电液卸载阀
DE102012214408A1 (de) 2011-09-16 2013-03-21 Robert Bosch Gmbh Verstelleinrichtung für eine hydrostatische Maschine und hydrostatische Maschine
FR2993940B1 (fr) * 2012-07-24 2018-11-09 Poclain Hydraulics Industrie Circuit de commande hydraulique avec securite en cas de coupure de commande
DE102016014361A1 (de) 2016-12-02 2018-06-07 Alpha Fluid Hydrauliksysteme Müller GmbH Proportionalventil in Hydrauliksystemen
DE102017222355A1 (de) * 2017-12-11 2019-06-13 Robert Bosch Gmbh Ansteuervorrichtung mit elektroproportionalem Regelverhalten und Doppel-Magnetspule
DE102021118806B3 (de) 2021-07-21 2022-10-13 Pierburg Pump Technology Gmbh Verfahren zur Steuerung einer elektrisch angetriebenen Fluidpumpe für ein Fahrzeug und eine elektrisch angetriebene Fluidpumpe für ein Fahrzeug

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3140397C2 (de) * 1981-10-10 1993-10-21 Bosch Gmbh Robert Vorgesteuerte Vorrichtung zur lastunabhängigen Regelung eines Druckmittelstroms proportional zu einem elektrischen Eingangssignal
US4801247A (en) * 1985-09-02 1989-01-31 Yuken Kogyo Kabushiki Kaisha Variable displacement piston pump
DE4115606A1 (de) * 1991-05-14 1992-11-19 Putzmeister Maschf Ueberlast-schutzeinrichtung fuer einen als brennkraftmaschine ausgebildeten antriebsmotor einer hauptpumpe eines hydraulischen druckversorgungsaggregats
DE4327313C2 (de) * 1993-08-13 2001-07-05 Mannesmann Rexroth Ag Verfahren zur Druckregelung einer hydrostatischen Maschine mit verstellbarem Fördervolumen
DE4410719A1 (de) * 1994-03-28 1995-10-05 Bosch Gmbh Robert Elektrohydraulisch verstellbare Pumpe

Also Published As

Publication number Publication date
DE59809947D1 (de) 2003-11-27
JPH1150968A (ja) 1999-02-23
EP0884476A3 (fr) 1999-02-03
EP0884476A2 (fr) 1998-12-16
DE19724870A1 (de) 1998-12-17

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