EP0600918A1 - Dispositif de reglage hydraulique. - Google Patents

Dispositif de reglage hydraulique.

Info

Publication number
EP0600918A1
EP0600918A1 EP92915854A EP92915854A EP0600918A1 EP 0600918 A1 EP0600918 A1 EP 0600918A1 EP 92915854 A EP92915854 A EP 92915854A EP 92915854 A EP92915854 A EP 92915854A EP 0600918 A1 EP0600918 A1 EP 0600918A1
Authority
EP
European Patent Office
Prior art keywords
pressure
valve
actuating device
hydraulic actuating
control valve
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
EP92915854A
Other languages
German (de)
English (en)
Other versions
EP0600918B1 (fr
Inventor
Manfred Ruoff
Helmut Rembold
Berthold Pfuhl
Volkmar Leutner
Martin Mueller
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 EP0600918A1 publication Critical patent/EP0600918A1/fr
Application granted granted Critical
Publication of EP0600918B1 publication Critical patent/EP0600918B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Classifications

    • 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
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • 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
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/3056—Assemblies of multiple valves
    • F15B2211/30565—Assemblies of multiple valves having multiple valves for a single output member, e.g. for creating higher valve function by use of multiple valves like two 2/2-valves replacing a 5/3-valve
    • F15B2211/30575—Assemblies of multiple valves having multiple valves for a single output member, e.g. for creating higher valve function by use of multiple valves like two 2/2-valves replacing a 5/3-valve in a Wheatstone Bridge arrangement (also half bridges)
    • 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
    • F15B2211/40—Flow control
    • F15B2211/415—Flow control characterised by the connections of the flow control means in the circuit
    • F15B2211/41527—Flow control characterised by the connections of the flow control means in the circuit being connected to an output member and a directional control valve
    • F15B2211/41536—Flow control characterised by the connections of the flow control means in the circuit being connected to an output member and a directional control valve being connected to multiple ports of an output member
    • 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
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
    • F15B2211/50518—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using pressure relief valves
    • 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
    • F15B2211/50—Pressure control
    • F15B2211/515—Pressure control characterised by the connections of the pressure control means in the circuit
    • F15B2211/5153—Pressure control characterised by the connections of the pressure control means in the circuit being connected to an output member and a directional control valve
    • F15B2211/5154—Pressure control characterised by the connections of the pressure control means in the circuit being connected to an output member and a directional control valve being connected to multiple ports of an output member
    • 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
    • F15B2211/50—Pressure control
    • F15B2211/515—Pressure control characterised by the connections of the pressure control means in the circuit
    • F15B2211/5158—Pressure control characterised by the connections of the pressure control means in the circuit being connected to a pressure source and an output member
    • 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
    • F15B2211/50—Pressure control
    • F15B2211/515—Pressure control characterised by the connections of the pressure control means in the circuit
    • F15B2211/5159—Pressure control characterised by the connections of the pressure control means in the circuit being connected to an output member and a return line
    • 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
    • F15B2211/50—Pressure control
    • F15B2211/52—Pressure control characterised by the type of actuation
    • F15B2211/526—Pressure control characterised by the type of actuation electrically or electronically
    • 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
    • F15B2211/50—Pressure control
    • F15B2211/52—Pressure control characterised by the type of actuation
    • F15B2211/528—Pressure control characterised by the type of actuation actuated by fluid pressure

Definitions

  • the invention is based on a hydraulic actuator according to the preamble of the main claim.
  • a hydraulic control device is known from DE-OS 40 37 834, in which the partial pressures in the pressure chambers of a differential cylinder can be changed via an electromagnetically actuated control valve.
  • the partial pressures in the pressure chambers are set by partial discharge of pressure medium, these partial pressures being kept approximately constant by appropriate control of the control valve.
  • the control valve is actuated in such a way that the holding pressures are very much lower than the adjustment pressures required for an adjustment movement.
  • the ring surface of the differential cylinder is always acted on by a pump with pressure medium, while the pressure in the pressure chamber on the large piston surface can be changed by the electromagnetically actuated control valve.
  • the control valve is designed as a 3/2-way valve and in a line connection between the pump and the Pressure chamber switched on the large piston area.
  • Such a hydraulic actuating device is used, for example, to actuate a device for adjusting the camshaft relative to the crankshaft in an internal combustion engine (DE-OS 36 16 234).
  • DE-OS 36 16 234 internal combustion engine
  • narrow and long guide gaps are sometimes necessary for the valve member in these control valves.
  • these control valves may be sensitive to dirt, ie if the pressure medium (engine oil from the internal combustion engine) is contaminated, the valve function may be impaired.
  • the hydraulic actuator according to the invention with the characterizing features of the main claim has the advantage that it works with low losses if there is no adjustment movement of the differential piston, that it is simple and that the sensitivity of the control valve to contamination is low.
  • FIGS. 1 and 2 show in FIGS. 1 and 2 an exemplary embodiment of a hydraulic actuating device in a simplified representation. Description of the embodiments
  • 10 denotes a hydraulic actuating device which has a differential cylinder 11 with differential pistons 12, 13.
  • the pressure chamber 14 on the annular surface of the differential cylinder is always acted upon via a pressure line 15 by a pump 16 which is driven by a drive shaft 17, for example the camshaft of an internal combustion engine.
  • the pressure chamber 18 on the larger effective piston surface of the differential cylinder is connected via a line 19 to the inlet 20 of a pressure relief valve 21.
  • This has a pressure chamber 23 formed in a valve housing 22, only indicated, in which a valve member 24 is arranged, which cooperates with a valve seat 25 at the inlet 20.
  • the pressure chamber 23 of the pressure relief valve 21 is connected to a container 27 via a return line 26.
  • the pressure chamber 23 merges on the side opposite the valve seat 25 into a longitudinal bore 29 which is closed by the housing 30 of a proportional magnet 31.
  • Two annular control grooves 32, 33 extend around the longitudinal bore 29 at a distance from one another.
  • a control slide 34 is arranged in the interior of the longitudinal bore 29 and has a circumferential annular groove 35 running in the central area thereof, which, in a manner still to be explained, with the control grooves 32, 33 cooperates.
  • the actuating plunger 37 of the proportional magnet 31 bears against the lower end face 36 of the control slide 34.
  • One end of a compression spring 39 rests on the upper end face 38, the opposite end of which is supported on the valve member 24.
  • a connecting line 41 branches off from the pressure line 19 and connects to the pressure line 15 via an interposed throttle 42 connected is.
  • a first bypass line 43 leads from the pressure line 19 to the lower control groove 33 in the valve housing 22.
  • a second bypass line 44 extends from the upper control groove 32 and opens into the connecting line 41 between the throttle 42 and the pressure line 15.
  • the hydraulic actuating device 10 is used, for example, in a device for continuously adjusting the camshaft of an internal combustion engine relative to its crankshaft, as a result of which a phase shift is generated between these two shafts.
  • the pressure control valve 21 actuated by the proportional magnet 31 serves as the active control element of the hydraulic actuating device.
  • the proportional magnet 31 is not energized in the position shown, ie. h, the actuating plunger 37 and the control slide 34 are in their lower neutral position.
  • a force is exerted on the valve member 24 only because of the pretension of the compression spring 39, which pushes it against the valve seat 25.
  • This (residual) bias is relatively low, i. H. the compression spring 39 is almost completely relaxed.
  • the annular groove 35 of the control slide 34 is located in the region of the lower control groove 33 in the longitudinal bore 29 of the valve housing 22.
  • the upper control groove 32 is closed off by the control slide 34 against the lower control groove 33.
  • the pressure chamber 14 of the differential cylinder 11 is pressurized directly by the pump 16 via the pressure line 15.
  • the pump 16 is advantageously provided with a suction throttling to limit the flow rate.
  • the pressure chamber 18 on the large piston area of the differential piston 12 is connected via the pressure line 19 to the inlet 20 of the pressure relief valve 21.
  • This pressure line 19 is also connected via the connecting line 41 Intermediate throttle 42 connected to the pressure line 15.
  • the two bypass lines 43, 44 are meanwhile closed on one side by the control slide 34.
  • a pressure builds up in the pressure chamber 14 via the pressure line 15, which pressure corresponds to the dynamic pressure upstream of the throttle 42 in the line 41.
  • the pressure relief valve 21 opens. H. the valve member 24 lifts off the valve seat 25, so that a connection is created via the pressure chamber 23 and the return line 26 to the container 27.
  • the differential piston is displaced to the left by the pressure acting in the pressure chamber 14.
  • this movement of the differential piston means an adjustment of the camshaft to "late”, ie. H. to a late turning position or later valve actuation.
  • the differential piston 12, 13 To adjust to "early" or earlier rotational position, the differential piston 12, 13 must be moved to the right.
  • the proportional magnet 31 is excited so that the actuating plunger 37 and thus the control slide 34 move upward.
  • the bias of the compression spring 39 and thus the opening pressure of the pressure relief valve 21 is increased so that a higher pressure can build up in the pressure chamber 18.
  • the control groove 32 and 33 are connected in the longitudinal bore 29 via the annular groove 35 of the control slide. This creates a bypass to the throttle 42 via the bypass lines 44 and 43, so that the pressure chamber 18 on the larger piston surface of the differential cylinder via the lines 43 and 44 and the connecting line 41 is connected to the pressure line 15 bypassing the throttle 42. Due to the larger effective piston area, the differential piston 12, 13 is moved to the right. By bypassing the throttle
  • the pressure at the pressure limiting valve 21 is set via appropriate excitation (less current) of the proportional magnet 31 so that the resultant force on the differential piston, due to the pressures in the two pressure chambers, is precisely the restoring force from the device for adjusting the camshaft corresponds.
  • Appropriate control of the proportional solenoids also ensures that these holding pressures are kept at a level which changes just enough to absorb the restoring forces from the device for adjusting the camshaft even when the rotational speed of the camshaft changes.
  • pressure relief valve 21 As an active control element, long sealing gaps and tight fits for high-pressure sealing are avoided. So that is the sensitivity to contamination low, so that the hydraulic actuating device is particularly well suited for use in internal combustion engines with engine oil contaminated due to operation.
  • FIG. 2 describes a modification of the above exemplary embodiment, in which the throttle in the connection between the two pressure lines is replaced by a passive pressure relief valve.
  • the two pressure lines 15 and 19 are connected by two connecting line sections 41a, 41b.
  • the line section 41a leads from the pressure line 15 to the inlet 46 of the passive pressure relief valve 47. From its outlet 48, the connecting line 41b leads to the pressure line 19.
  • the passive pressure relief valve 47 has a cylindrical valve chamber 50 which opens into a conical pressure chamber 51.
  • a cylindrical valve member 52 is guided in the valve chamber 50, the upper end face 53 of which cooperates with the conical surface 54 of the pressure chamber.
  • the part of the valve chamber that receives the compression spring is connected to a container 59 via a leak oil line 58.
  • the inlet 46 of the pressure relief valve is arranged on the pressure chamber in such a way that it interacts with the end face of the valve member, the outlet is arranged below it in the area of the outer surface of the valve member.
  • the pressure limiting valve 21a is regulated directly by the proportional magnet 31 via the compression spring 39a; a control slide valve - as in FIG. 1 - is not interposed.
  • the proportional magnet When the proportional magnet is de-energized, the pressure of approximately 30 bar required to move the differential cylinder to the left ("late") builds up in the pressure chamber 14 assigned to the annular surface of the differential cylinder.
  • the bias of the passive pressure relief valve 47 is set accordingly, so that the pressure chamber 18 is practically depressurized.
  • the bias of the compression spring 39a is increased by appropriate control of the proportional magnet, so that the pressure in the pressure line 15 and the connecting lines 41a, 41b increases.
  • the passive pressure relief valve 47 opens completely. The released cross-section is dimensioned so that no significant throttle loss occurs.
  • the pressure relief valve can also be designed as a seat valve with a freely guided valve member.
  • the pressure set on the control valve 21s then acts on the rear side (output side) of the valve member.
  • a 2/2-way valve can also be used as the active control element instead of the pressure limiting valve 21a, which valve is actuated in pulsed form by an electromagnet. The pressure control then takes place via control or regulation of the volume flow.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Valve Device For Special Equipments (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)

Abstract

Le dispositif de réglage hydraulique présente un cylindre à différentiel (11) dont l'espace annulaire (14) est toujours alimenté en pression par une pompe (16). La chambre de pression (18) en face de la grande surface du piston est reliée par une conduite de connexion (41) à la pompe. De cette conduite de connexion (41) part une dérivation menant à une soupape de commande (21). Cette soupape de commande est d'autre part en communication avec une conduite de retour (26). Par pilotage approprié de la soupape de commande il est possible de faire varier la pression dans la dérivation (19) et par conséquent dans les chambres de pression (14, 18) du cylindre à différentiel.
EP92915854A 1991-08-29 1992-07-30 Dispositif de reglage hydraulique Expired - Lifetime EP0600918B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE4128656A DE4128656C2 (de) 1991-08-29 1991-08-29 Hydraulische Stelleinrichtung und deren Verwendung
DE4128656 1991-08-29
PCT/DE1992/000622 WO1993005302A1 (fr) 1991-08-29 1992-07-30 Dispositif de reglage hydraulique

Publications (2)

Publication Number Publication Date
EP0600918A1 true EP0600918A1 (fr) 1994-06-15
EP0600918B1 EP0600918B1 (fr) 1997-01-22

Family

ID=6439381

Family Applications (1)

Application Number Title Priority Date Filing Date
EP92915854A Expired - Lifetime EP0600918B1 (fr) 1991-08-29 1992-07-30 Dispositif de reglage hydraulique

Country Status (6)

Country Link
US (1) US5421294A (fr)
EP (1) EP0600918B1 (fr)
JP (1) JP3536077B2 (fr)
KR (1) KR100225994B1 (fr)
DE (2) DE4128656C2 (fr)
WO (1) WO1993005302A1 (fr)

Families Citing this family (11)

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US5615648A (en) * 1992-07-25 1997-04-01 Robert Bosch Gmbh Electro-hydraulic adjusting device
DE4240075C2 (de) * 1992-11-28 2002-08-29 Bosch Gmbh Robert Hydraulische Stelleinrichtung
DE19505741A1 (de) * 1995-02-20 1996-08-22 Schaeffler Waelzlager Kg Anordnung zur Vermeidung von Startgeräuschen bei Nockenverstellern
DE19630712A1 (de) * 1996-07-30 1998-02-05 Rexroth Mannesmann Gmbh Vorschubhydraulik
DE19756016A1 (de) * 1997-12-17 1999-06-24 Porsche Ag Vorrichtung zur hydraulischen Drehwinkelverstellung einer Welle zu einem Antriebsrad
JP3962670B2 (ja) * 2002-10-25 2007-08-22 株式会社アーステクニカ 旋動式破砕機の油圧回路およびその油圧回路の制御方法
US7305914B2 (en) * 2004-01-28 2007-12-11 The United States Of America, As Represented By The Administrator Of The Environmental Protection Agency Hydraulic actuator control valve
US7364198B2 (en) * 2004-10-22 2008-04-29 Trw Automotive U.S. Llc Steering column locking mechanism
KR101536571B1 (ko) * 2013-09-25 2015-07-14 최병열 유압실린더의 유압 조절장치
SE2150207A1 (en) * 2021-02-26 2022-03-01 Vaederstad Holding Ab Control of linear actuators
KR20260000025A (ko) 2024-06-24 2026-01-02 주식회사김스애드 접근 감지 도로 반사경

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Also Published As

Publication number Publication date
DE4128656A1 (de) 1993-03-04
DE4128656C2 (de) 1994-10-20
WO1993005302A1 (fr) 1993-03-18
US5421294A (en) 1995-06-06
JP3536077B2 (ja) 2004-06-07
KR100225994B1 (ko) 1999-10-15
JPH06510106A (ja) 1994-11-10
KR940702252A (ko) 1994-07-28
EP0600918B1 (fr) 1997-01-22
DE59207959D1 (de) 1997-03-06

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