EP2365226A1 - Hydraulikanlage - Google Patents

Hydraulikanlage Download PDF

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Publication number
EP2365226A1
EP2365226A1 EP11157419A EP11157419A EP2365226A1 EP 2365226 A1 EP2365226 A1 EP 2365226A1 EP 11157419 A EP11157419 A EP 11157419A EP 11157419 A EP11157419 A EP 11157419A EP 2365226 A1 EP2365226 A1 EP 2365226A1
Authority
EP
European Patent Office
Prior art keywords
port
valve
pressure
spool
return
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
EP11157419A
Other languages
English (en)
French (fr)
Other versions
EP2365226B1 (de
Inventor
Ricccardo Morselli
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.)
CNH Industrial Italia SpA
Original Assignee
CNH Industrial Italia SpA
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 CNH Industrial Italia SpA filed Critical CNH Industrial Italia SpA
Publication of EP2365226A1 publication Critical patent/EP2365226A1/de
Application granted granted Critical
Publication of EP2365226B1 publication Critical patent/EP2365226B1/de
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • F15B11/04—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
    • F15B11/044—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the return line, i.e. "meter out"
    • 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
    • F15B2211/31—Directional control characterised by the positions of the valve element
    • F15B2211/3122—Special positions other than the pump port being connected to working ports or the working ports being connected to the return line
    • F15B2211/3127—Floating position connecting the working ports and the 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
    • F15B2211/40—Flow control
    • F15B2211/415—Flow control characterised by the connections of the flow control means in the circuit
    • F15B2211/41581—Flow control characterised by the connections of the flow 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
    • F15B2211/40—Flow control
    • F15B2211/42—Flow control characterised by the type of actuation
    • F15B2211/428—Flow control characterised by the type of actuation actuated by fluid 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
    • F15B2211/76—Control of force or torque of the output member
    • F15B2211/761—Control of a negative load, i.e. of a load generating hydraulic energy
    • 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
    • F15B2211/77—Control of direction of movement of the output member
    • F15B2211/7741—Control of direction of movement of the output member with floating mode, e.g. using a direct connection between both lines of a double-acting cylinder

Definitions

  • the present invention relates to a hydraulic system for controlling the supply of hydraulic power to a load, such as a jack.
  • Tractors and other agricultural vehicles often have hydraulic output lines, sometimes termed an electro-hydraulic remote, which are used to supply hydraulic power to ancillary equipment.
  • Two output lines are used, one to supply hydraulic fluid under pressure and the other acts a return line for the fluid discharged by the load.
  • Each of these two output lines is connectible by a leak proof coupling to a hose leading to a respective side of the load.
  • FIG. 1A to 1D which schematic show a prior art valve with the spool in four different positions.
  • the two output ports A and B of the spool valve 10 lead to two output lines connectable to the load 12.
  • a first port R is connected to a return line leading to a fluid reservoir
  • a second port PC is connected to a source of pressurised fluid
  • the third port PLS is connected to a sensing line for allowing the back pressure to be monitored.
  • Figure 1B the spool is shown in its position to extend the jack 12. Fluid under pressure is supplied from the supply port PC to the working chamber on the right of the piston of the jack 12 while fluid from the other working chamber is allowed to return to the reservoir through the return port R, causing the piston to move from right to left as viewed.
  • the load sensing port PLS is connected to the return port R when the cylinder is locked or floating.
  • the load sensing port PLS is connected to the output port A or B that is connected to the supply port PC.
  • throttles are provided in the connections leading from the supply port PC to the respective output port A or B. The purpose of each throttle in the spool is not to damp the movement of the load but merely to allow a load sensing pressure difference to be developed across it indicative of the resistance offered by the load. If the load is low and the piston moves freely, there will be a high flow rate in the throttle and the pressure measured at the port PLS will be lower than the supply pressure PC. However, when the load offers high resistance, the flow rate through the throttle will be low and the sensed pressure PLS will be nearly equal to supply pressure PC.
  • the present invention seeks therefore to provide a hydraulic system which operates efficiently when the controlled load is operating in a resistive mode yet provides hydraulic damping then the load is operating in a draft mode.
  • a hydraulic system having a spool valve with two output ports connectible to opposite sides of a hydraulic load and three input ports which include a supply port connectable to a pressure supply line, a return port connectable to a return line, wherein a first throttle is provided in the flow path between the pressure supply line and each output port, the downstream side of the first throttle being connected to the pressure sensing port, and a second throttle is provided in the flow path from each output port to the return line, characterised in that a low resistance discharge path bypassing the valve spool is provided between at least one of the output ports and the return port, the low resistance discharge path including a normally closed valve that opens when the pressure difference between the sensing port and the output port exceeds a predetermined level.
  • the sensing port when the sensing port is at a lower pressure than the return side of the load, indicating that the load is a draft load, the low resistance discharge path remains closed and the fluid from the return side of the load has to pass the throttled flow path through the spool valve before reaching the reservoir, resulting in damping of the movement of the load.
  • the sensing port is at a higher pressure than the output port, indicating a resistive load, the discharge path is opened so that less resistance to flow is offered by the fluid returning to the reservoir and an improved efficiency is achieved.
  • the normally closed valve is preferably a hydraulically controlled spool valve urged by a spring towards a closed position, the spool being moved towards the open position by the pressure at the sensing port and towards the closed position by the pressure at the output port.
  • each of the output ports may have a respective discharge path incorporating a respective normally closed valve.
  • FIG 2 shows the spool valve 10 in the same position as in Figure 1B .
  • the passage in the valve spool connecting the output port B to return line R is shown as incorporating a throttle but this throttle may alternatively be disposed with the return port.
  • This throttle offers resistance to flow to damp the movement of the load when it is operating in a draft mode.
  • the system of the invention shown in Figure 2 overcomes this energy waste by providing two flow paths for the return fluid.
  • One flow path has a higher resistance to provide damping when operating in draft mode and the other having lower resistance when operating in resistive mode.
  • the switching between flow paths is automatic and requires no intervention from the operator.
  • a hydraulically controlled on/off spool valve 24 is provided in a low resistance discharge line 22 leading from the port B to the reservoir. Under normal condition, this valve 24 is closed as represented by the spring at the left of the valve in Figure 2 .
  • the spool of the valve 24 is urged in a direction to close by the pressure in the port B and is urged in a direction to open by the pressure PLS in the sensing port.
  • the sensed back pressure will be greater than the pressure in the return port and when the net force on the spool of the valve 24 exceeds the spring force, the spool 24 moves to the left as shown and opens the valve 24. This opening immediately reduces the pressure in port B to nearly ambient pressure and as long as the sensed back pressure remains sufficient to overcome the return spring acting on the spool, the valve 24 will remain open.
  • valve 34 serves the same function as the valve 24 but is only active when the spool of the valve 10 is moved to the position shown in Figure 1C .
  • port A is under the same pressure as the back pressure PLS in the sensing port and the valve 34 is therefore kept in its closed position by the action of its own spring.
  • a hydraulic motor can have a draft mode when attempting to reduce the speed of a flywheel having a high moment of inertia.
  • the embodiment of the invention shown in Figure 3 is essentially the same as that of Figure 2 save for the addition of an electronically controlled discharge valve 44 which allows the discharge flow through the valves 24 and 34 to be enabled and disabled.
  • the discharge valve 44 When the discharge valve 44 is closed, the hydraulic system behaves in the same way as a conventional system, as described above by reference to Figures 1A to 1D .
  • the valve 44 when the valve 44 is opened, the hydraulic system behaves in the same manner as the embodiment of the invention shown in Figure 2 .
  • the advantages offered by this additional control are that it results in smooth transitions when one of the valves 24 and 34 opens and it allows disablement of the discharge flows which bypass the spool valve 10, when necessary for safety or specific working conditions.
  • a throttle may be provided in series with the supply line instead of two throttles being integrated into the valve spool.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)
EP11157419.0A 2010-03-12 2011-03-09 Hydraulikanlage Active EP2365226B1 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
IT000190A ITTO20100190A1 (it) 2010-03-12 2010-03-12 Sistema idraulico

Publications (2)

Publication Number Publication Date
EP2365226A1 true EP2365226A1 (de) 2011-09-14
EP2365226B1 EP2365226B1 (de) 2013-05-22

Family

ID=43016653

Family Applications (1)

Application Number Title Priority Date Filing Date
EP11157419.0A Active EP2365226B1 (de) 2010-03-12 2011-03-09 Hydraulikanlage

Country Status (2)

Country Link
EP (1) EP2365226B1 (de)
IT (1) ITTO20100190A1 (de)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2013095926A1 (en) * 2011-12-23 2013-06-27 Caterpillar Inc. Hydraulic system for controlling a work implement
WO2014060645A1 (en) * 2012-10-18 2014-04-24 Wärtsilä Finland Oy Gas exchange valve arrangement
EP3001042A1 (de) * 2014-09-25 2016-03-30 CNH Industrial Italia S.p.A. Hydraulikanlage
EP3001043A1 (de) * 2014-09-25 2016-03-30 CNH Industrial Italia S.p.A. Hydraulikventil
IT201900015363A1 (it) * 2019-09-02 2021-03-02 Cnh Ind Italia Spa Valvola direzionale per un veicolo da lavoro e relativa disposizione idraulica

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0251172A2 (de) * 1986-06-30 1988-01-07 Vickers Incorporated Hydraulisches Steuersystem
US6092454A (en) * 1998-07-23 2000-07-25 Caterpillar Inc. Controlled float circuit for an actuator
WO2004042235A1 (de) * 2002-11-07 2004-05-21 Bosch Rexroth Ag Hydraulisches zweikreisbremssystem
DE102005022275A1 (de) * 2004-07-22 2006-02-16 Bosch Rexroth Aktiengesellschaft Hydraulische Steueranordnung

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0251172A2 (de) * 1986-06-30 1988-01-07 Vickers Incorporated Hydraulisches Steuersystem
US6092454A (en) * 1998-07-23 2000-07-25 Caterpillar Inc. Controlled float circuit for an actuator
WO2004042235A1 (de) * 2002-11-07 2004-05-21 Bosch Rexroth Ag Hydraulisches zweikreisbremssystem
DE102005022275A1 (de) * 2004-07-22 2006-02-16 Bosch Rexroth Aktiengesellschaft Hydraulische Steueranordnung

Cited By (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2013095926A1 (en) * 2011-12-23 2013-06-27 Caterpillar Inc. Hydraulic system for controlling a work implement
US9085873B2 (en) 2011-12-23 2015-07-21 Caterpillar Inc. Hydraulic system for controlling a work implement
WO2014060645A1 (en) * 2012-10-18 2014-04-24 Wärtsilä Finland Oy Gas exchange valve arrangement
CN104822911A (zh) * 2012-10-18 2015-08-05 瓦锡兰芬兰有限公司 气体交换阀装置
CN105465064A (zh) * 2014-09-25 2016-04-06 凯斯纽荷兰(中国)管理有限公司 液压系统
EP3001043A1 (de) * 2014-09-25 2016-03-30 CNH Industrial Italia S.p.A. Hydraulikventil
US20160090716A1 (en) * 2014-09-25 2016-03-31 CNH Industrial America, LLC Hydraulic valve
US20160090997A1 (en) * 2014-09-25 2016-03-31 CNH Industrial America, LLC Hydraulic system
EP3001042A1 (de) * 2014-09-25 2016-03-30 CNH Industrial Italia S.p.A. Hydraulikanlage
CN105465076A (zh) * 2014-09-25 2016-04-06 凯斯纽荷兰(中国)管理有限公司 液压阀
US9708796B2 (en) 2014-09-25 2017-07-18 Cnh Industrial America Llc Hydraulic valve
US9790964B2 (en) 2014-09-25 2017-10-17 Cnh Industrial America Llc Hydraulic system
CN105465064B (zh) * 2014-09-25 2019-01-22 凯斯纽荷兰(中国)管理有限公司 液压系统
CN105465076B (zh) * 2014-09-25 2019-01-22 凯斯纽荷兰(中国)管理有限公司 液压阀
IT201900015363A1 (it) * 2019-09-02 2021-03-02 Cnh Ind Italia Spa Valvola direzionale per un veicolo da lavoro e relativa disposizione idraulica
EP3786461A1 (de) * 2019-09-02 2021-03-03 CNH Industrial Italia S.p.A. Wegeventil für ein arbeitsfahrzeug und zugehörige hydraulische anordnung

Also Published As

Publication number Publication date
EP2365226B1 (de) 2013-05-22
ITTO20100190A1 (it) 2011-09-13

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