WO2011072772A1 - Circuit de détection de charge - Google Patents

Circuit de détection de charge Download PDF

Info

Publication number
WO2011072772A1
WO2011072772A1 PCT/EP2010/006551 EP2010006551W WO2011072772A1 WO 2011072772 A1 WO2011072772 A1 WO 2011072772A1 EP 2010006551 W EP2010006551 W EP 2010006551W WO 2011072772 A1 WO2011072772 A1 WO 2011072772A1
Authority
WO
WIPO (PCT)
Prior art keywords
pressure
load
valve
load detection
piston
Prior art date
Application number
PCT/EP2010/006551
Other languages
German (de)
English (en)
Inventor
Edwin Heemskerk
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 WO2011072772A1 publication Critical patent/WO2011072772A1/fr

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
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/0416—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor with means or adapted for load sensing
    • 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
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/605—Load sensing circuits
    • F15B2211/6051—Load sensing circuits having valve means between output member and the load sensing circuit
    • 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
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/65—Methods of control of the load sensing pressure
    • F15B2211/651—Methods of control of the load sensing pressure characterised by the way the load pressure is communicated to the load sensing circuit
    • 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
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/65—Methods of control of the load sensing pressure
    • F15B2211/654—Methods of control of the load sensing pressure the load sensing pressure being lower than the load pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
    • F15B2211/7051—Linear output members
    • F15B2211/7053—Double-acting output members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/76—Control of force or torque of the output member
    • F15B2211/761—Control of a negative load, i.e. of a load generating hydraulic energy

Definitions

  • the present invention relates to a load detection circuit having a load detection valve for detecting and converting a load pressure prevailing at a load into a (reference) pressure usable for controlling a hydraulic system.
  • This signal in turn serves as a reference pressure signal for controlling / regulating hydraulic system own components such as a hydraulic pump, control valves, etc.
  • the stepped piston according to FIG. 4 may be mentioned here.
  • Such a stepped piston has the same area ratio as the example as
  • FIG. 5 Another solution example is shown in FIG. 5, from which a preferably designed as a hydraulic cylinder consumer can be removed, at the ring and piston chamber each one Pressure sensor is connected. Depending on the pressure load within the ring and piston chambers, both sensors generate an electrical signal which is fed to an electronic control unit which calculates the net pull / pressure load from this and a representative (electrical)
  • Reference pressure signal is generated.
  • the electrical reference pressure signal When such a signal is to be used, for example, to actuate a hydraulic-mechanical valve, the electrical reference pressure signal must first be converted back into a hydraulic signal by means of a further valve. This is expensive and requires appropriate space for the arrangement of the necessary valves. Also, not every control, in particular in mobile hydraulics, has corresponding control electronics. Incidentally, the same applies to stationary hydraulic drives.
  • Hydraulic pump to be adapted to the conditions required by a consumer.
  • the controlled variable is the pressure drop across a consumer control valve (proportional valve) of the hydraulic system.
  • a pressure regulating valve is displaced, via which a hydraulic actuating cylinder of a variable displacement pump is actuated.
  • Variable displacement pump can be used. In view of this problem, it is the object of the present invention, without the
  • Control / regulation of a hydraulic system can be used. More specifically, a load detection valve (pressure valve) is provided, which is acted upon at its two control sides with the pressure in both chambers of a cylinder as a consumer. Depending on whether a pulling or pushing load acts on a cylinder rod, a corresponding load (over) pressure (in particular a load pressure or a load overpressure) is applied to one of the two control sides, as a result of which the load detection valve has one of its two, traction or overpressures Pressure load indicating outputs with a net load
  • pressure chamber-shaped has a piston chamber pressure portion which is fluidly connected to a piston chamber of the cylinder and a fluid separated from the piston chamber pressure
  • Cylinder is connectable. Further, a second control side of the load detection valve has a (pressure-chamber-shaped) annular chamber pressure section connected to the annular chamber of the cylinder and a fluid-isolated (pressure-chamber-shaped) thereof.
  • Pressure load line section which is connectable to the piston chamber of the cylinder.
  • the load detection valve has a valve piston, which is displaceable depending on the current pressure situation on the two control sides (pressure difference) from a valve closing all neutral positions in a second switching position, in which
  • Piston chamber pressure portion of the first control side is connected to the pressure load line portion of the second control side and (or) is displaceable in a third switching position in which the annular chamber pressure portion of the second control side is connected to the Switzerlandlast effetsab songs the first control side.
  • this pressure in the associated pressure measuring chamber namely the pressure load line section or
  • Pull load line section as a representative (reference) pressure tap and provide the hydraulic control available.
  • the piston chamber pressure portion of the first control side and the pressure load line portion of the second control side the same pressure application area on the valve piston, which is different from the also same pressure application surface of the annular chamber pressure portion of the second control side and the Switzerlandlasttechnischsab songs the first control side.
  • the load detection valve can be matched to the geometric conditions of the cylinder, so that, for example, a pressure bias of the cylinder piston from the load detection valve is not displayed.
  • all of the above-mentioned pressure application surfaces can be the same.
  • FIG. 1 shows a hydraulic circuit for load detection by means of a load detection valve (pressure valve) according to a first preferred embodiment of the invention
  • FIG. 3 shows a hydraulic circuit for load detection by means of a load detection valve (pressure valve) according to a second preferred embodiment of the invention
  • FIG. 3 shows a longitudinal section of the load detection valve according to FIG.
  • Fig. 4 shows a stepped piston for load detection according to a prior art
  • Fig. 5 shows a pressure sensor arrangement for load detection according to the prior art.
  • a cylinder 1 shows schematically a hydraulic circuit with respect to the detection of a load acting on a cylinder by means of a load detection valve according to the invention.
  • a cylinder 1 has an annular chamber 1a and a piston chamber 1b, which are fluid-tightly separated from an axially movable (cylinder) piston 2.
  • the piston chamber 1 b is via a piston chamber line 4 and the annular chamber 1 a is via a
  • Ring chamber line 6 connected to a not further shown hydraulic system for actuating the cylinder 1.
  • a load detection valve 8 is connected to the piston chamber line 4 and the annular chamber line 6.
  • the load detection valve 8 here in the form of a proportional pressure valve, has two input ports 10, 12 and three output ports 14, 16, 18, of which a first output port 14 is a tank port. Furthermore, the load detection valve 8 has a first and second control side 20, 22, which are each biased by a spring and to the two control pressures separately (spatially separated) can be applied.
  • the first control side 20 has a (chamber-shaped) piston chamber pressure section 24, which via a first control line to the
  • Piston chamber line 4 is connected.
  • the second control side 22 has a
  • annular chamber pressure section 26 which is connected via a second control line to the annular chamber line 6. Both control lines are additionally connected to an input terminal 10, 12 of the load detection valve 8 and
  • the load detection valve 8 has an axially continuously displaceable valve piston 28 which is in the design position, i. in neutral position (center position of the valve piston, caused by the bilateral uniform spring preload), the two input ports 10, 12 and the three output ports 14-18 of the valve 8 locks.
  • Load detection valve 8 connected.
  • the pressure load section 34 and the tensile load section 36 are fluid-tightly separated from the annular chamber pressure section 26 and the piston chamber pressure section 24, respectively.
  • the load detection valve 8 With regard to the structural design of the load detection valve 8 according to the invention reference is made to FIG. 2 below.
  • the load detection valve 8 consists of a preferably two-part valve housing 38, in which a longitudinal bore is formed.
  • a longitudinal bore In the longitudinal bore of the valve piston 28th
  • a chamber is formed between the corresponding piston end face and the valve housing 38, which forms the Switzerlandlastabrough 36 of the first control side 20.
  • a biasing spring is used, which presses the valve piston 28 according to the figure 2 to the right.
  • the valve piston 28 has in its central portion a radially projecting shoulder 40, which forms on its the tensile load section 36 side edge facing another chamber with the housing 38, which represents the piston chamber pressure portion 24 of the first control side 20.
  • Piston chamber pressure section 24 facing away from side edge of the paragraph 40 forms this • with the housing 38, a third chamber, which is the pressure load portion 34 of the second control side 22.
  • the right in FIG. 2 end face of the valve piston 28 with the housing 38 forms a fourth chamber, which represents the annular chamber pressure section 26 of the second control side 22.
  • a spring is used, which presses the valve piston in a left direction according to FIG 2.
  • the engagement surfaces on the respective end faces of the valve piston 28 (in the chambers 26, 36) are mutually equal but different from those of the mentioned side edges on the radial piston shoulder 40 (in the chambers 24, 34 ), which in turn are equal to each other. The reason for this is that the respective attack surfaces (control window) on the valve piston 28 on the
  • Pressurization surfaces of the cylinder piston 2 must be tuned to, for example, in a pressure-loaded cylinder piston 2 (at rest) a
  • Cylinder piston 2 is smaller on the annular chamber side than on the piston chamber side.
  • a blind hole 42 is introduced, which is closed on the open side by means of a dummy plug.
  • this blind bore 42 opens a first radial bore 44 which is fluidly connected to the piston chamber pressure portion 24 of the first control side 20 and a second radial bore 46 which is fluidly connected to the pressure load portion 34 of the second control side 22 when the valve piston 28 of FIG. 2 to the right is moved.
  • a fluid channel 48 is incorporated, which opens at its one end in the Buchlastabsammlung 36 of the first control side 20 and which is fluid-connectable at its other end to the annular chamber pressure portion 26 of the second control side 22 when the valve piston 28 as shown in FIG. 2 is moved to the left.
  • the tank connection 14 is indicated, which is placed between the tension load section 36 of the first control side 20 and the piston chamber pressure section 24 of the first control side 20 and with a displacement of the valve piston 28 to the right (according to FIG. 2) the tensile load section 32 or at a displacement of the valve piston 28 to the left (as shown in FIG. 2) with the pressure load portion 30 of the second control side 22 via the blind bore 42 in the valve piston 28 is connected:
  • valve piston 28 is in a central position according to the figure 2 (construction position), then all ports are locked. If the valve piston 28 is displaced to the left, then the chamber 34 is connected to the tank connection 14 via the bores 42 and 44. At the same time, the chamber 36 is connected via indicated on the right end side of the piston 28 longitudinal grooves and the fluid channel 48 to the chamber 26.
  • Cylinder chambers 1a, 1b This pressure is also applied to the load detection valve 8 via the piston chamber line 4 and / or the annular chamber line 6 and ensures that the valve piston 28 is deflected in a corresponding direction.
  • the connection opens from the respectively pressurized cylinder chamber to
  • Pressure measuring chamber is closed again.
  • the springs arranged on both sides ensure in the pressure-balanced state for a centering of the valve piston 28 in its neutral position.
  • the pressure load line 30 or the train load line 32 connected to the second and third output ports 16, 18 of the valve 8 receives a pressure signal corresponding to the pressure in the tension load section 36 or the pressure load section 34 representing the (reference) pressure representing the load load.
  • the cylinder piston 2 is pressure-stressed:
  • Piston chamber pressure section 24 and the pressure load section 34 are the same size, the force application surface in the annular chamber pressure section 26, however, is adapted to the annular chamber 1a of the cylinder 1 (that is smaller), in which a 20bar piston biasing pressure prevails, now the pressure in the pressure load section 34 increases to 100bar. In this case prevails
  • Net pressure load It is both quantitatively in terms of pressure level as well as qualitatively implemented as a compressive load in a reference pressure.
  • FIG. 3 shows a second exemplary embodiment of the invention, wherein, in the following, only the differences from the first exemplary embodiment according to FIG.
  • Hydraulic cylinder 1 depending on the situation hydraulic fluid from the tank port 1 of
  • Load detection valve 8 flows (for example, in a reduction of the load or load change). Since the outflowing hydraulic fluid comes from the cylinder chambers, the consumer would slowly move in the direction of the load.
  • variable (adjustable) orifice 50 for example a 2/2-way valve, is interposed in the tank line or at the tank connection 14 according to the second exemplary embodiment of the invention.
  • this valve 50 it is possible to leave the load detection valve 8 only in operation, as long as it is for more

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)

Abstract

L'invention concerne un circuit de détection de charge comprenant une soupape de détection de charge (8) soumise, sur ses deux côtés de commande (20, 22), à la pression régnant dans les chambres d'un vérin (1) faisant office de consommateur. Selon qu'une tige du vérin est soumise à une charge exerçant une traction ou une compression, une (sur)pression de charge correspondante est appliquée à l'un des deux côtés de commande, ce qui entraîne l'exposition d'une des deux sorties (16, 18), indiquant une charge de traction ou de compression, de la soupape de détection de charge, à une pression représentant la charge nette, en tant que pression de référence.
PCT/EP2010/006551 2009-12-15 2010-10-27 Circuit de détection de charge WO2011072772A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102009058406.4 2009-12-15
DE200910058406 DE102009058406A1 (de) 2009-12-15 2009-12-15 Lasterkennungsschaltung

Publications (1)

Publication Number Publication Date
WO2011072772A1 true WO2011072772A1 (fr) 2011-06-23

Family

ID=43479498

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2010/006551 WO2011072772A1 (fr) 2009-12-15 2010-10-27 Circuit de détection de charge

Country Status (2)

Country Link
DE (1) DE102009058406A1 (fr)
WO (1) WO2011072772A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9879667B2 (en) * 2014-03-03 2018-01-30 Danfoss Power Solutions Inc. Variable load sense spring setting for axial piston open circuit pump
CN116066454A (zh) * 2022-12-14 2023-05-05 中联重科股份有限公司 自适应控制方法、装置及设备

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3221501A (en) * 1964-08-19 1965-12-07 Seamone Woodrow Power matched hydraulic servo-system
DE2235788A1 (de) * 1971-07-23 1973-02-08 Sperry Rand Ltd Regelvorrichtung fuer hydraulische stellvorrichtungen
US4793238A (en) * 1987-07-01 1988-12-27 Caterpillar Inc. Control signal blocking direction control valve in load-sensing circuit
US6216456B1 (en) * 1999-11-15 2001-04-17 Caterpillar Inc. Load sensing hydraulic control system for variable displacement pump

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3221501A (en) * 1964-08-19 1965-12-07 Seamone Woodrow Power matched hydraulic servo-system
DE2235788A1 (de) * 1971-07-23 1973-02-08 Sperry Rand Ltd Regelvorrichtung fuer hydraulische stellvorrichtungen
US4793238A (en) * 1987-07-01 1988-12-27 Caterpillar Inc. Control signal blocking direction control valve in load-sensing circuit
US6216456B1 (en) * 1999-11-15 2001-04-17 Caterpillar Inc. Load sensing hydraulic control system for variable displacement pump

Also Published As

Publication number Publication date
DE102009058406A1 (de) 2011-06-16

Similar Documents

Publication Publication Date Title
EP2921924B1 (fr) Dispositif permettant de fournir un fluide avec régulation de la pression de sortie
DE102009017506A1 (de) Drucknachkompensiertes Hydrauliksteuerungsventil mit lastabhängiger Druckbegrenzung
EP2580507B1 (fr) Dispositif de soupape
EP2526307A1 (fr) Dispositif soupape
DE102008061350A1 (de) Hydrostatisches System mit einem hydropneumatischen Speicher
DE4108915C2 (de) Hydraulische Einrichtung zur Druckmittelversorgung eines bevorrechtigten Primärlastkreises
EP3018364B1 (fr) Dispositif de commande avec piston coulissant
DE102004025322A1 (de) Hydraulische Ventilanordnung
EP2268927A1 (fr) Système de commande destiné à commander un distributeur à plusieurs voies
WO2006105765A1 (fr) Soupape a tiroirs et dispositif de commande equipe de ladite soupape
WO2011072772A1 (fr) Circuit de détection de charge
DE102013206977A1 (de) Stromregelventilbaugruppe
DE4446538A1 (de) Hydraulische Spanneinrichtung
DE69302443T2 (de) Steuervorrichtung für mehrere hydraulische Verbraucher
WO2003087585A1 (fr) Systeme de commande hydraulique faisant appel au principe de la sensibilite de charge
EP2157320B1 (fr) Commande hydraulique pour un moteur hydraulique
DE102008052338B3 (de) Hydraulische Schaltung zum Zentrieren von Steuerkolben/Bypassschaltung für elektrisch-proportionale Verstellungen
EP1369596B1 (fr) Agencement de distributeur hydraulique
DE4418881A1 (de) Hubwerkregelsystem mit Regelventil
DE10224740B4 (de) Hydraulische Steuerventileinrichtung mit einer Stromregeleinrichtung
DE102015209657A1 (de) Hydraulische Ventilanordnung, hydraulischer Ventilblock mit einer derartigen Ventilanordnung, und hydraulischer Antrieb damit
DE4219552C2 (de) Vorgesteuertes Zwei-Wegeventil mit einstellbarer, druckunabhängiger Schließzeit
DE102004023553B3 (de) Hydraulik-Ventilanordnung, insbesondere Wasserhydraulik-Ventilanordnung
DE1751959C3 (de) Druckübertragungsvorrichtung
DE19625348A1 (de) Anordnung zur Ansteuerung eines hydraulisch betätigbaren Hauptventils

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 10778858

Country of ref document: EP

Kind code of ref document: A1

122 Ep: pct application non-entry in european phase

Ref document number: 10778858

Country of ref document: EP

Kind code of ref document: A1