CN104379972A - Hydraulic drive - Google Patents
Hydraulic drive Download PDFInfo
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- CN104379972A CN104379972A CN201380034063.2A CN201380034063A CN104379972A CN 104379972 A CN104379972 A CN 104379972A CN 201380034063 A CN201380034063 A CN 201380034063A CN 104379972 A CN104379972 A CN 104379972A
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- pressure
- valve
- drive unit
- limit
- joint
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/38—Control of exclusively fluid gearing
- F16H61/40—Control of exclusively fluid gearing hydrostatic
- F16H61/4148—Open loop circuits
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- 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"
- F15B11/0445—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" with counterbalance valves, e.g. to prevent overrunning or for braking
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/38—Control of exclusively fluid gearing
- F16H61/40—Control of exclusively fluid gearing hydrostatic
- F16H61/4157—Control of braking, e.g. preventing pump over-speeding when motor acts as a pump
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/38—Control of exclusively fluid gearing
- F16H61/40—Control of exclusively fluid gearing hydrostatic
- F16H61/46—Automatic regulation in accordance with output requirements
- F16H61/461—Automatic regulation in accordance with output requirements not involving a variation of the output capacity of the main pumps or motors
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/38—Control of exclusively fluid gearing
- F16H61/40—Control of exclusively fluid gearing hydrostatic
- F16H61/46—Automatic regulation in accordance with output requirements
- F16H61/47—Automatic regulation in accordance with output requirements for achieving a target output speed
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- 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
- F15B2211/50563—Pressure control characterised by the type of pressure control means the pressure control means controlling a differential pressure
- F15B2211/50581—Pressure control characterised by the type of pressure control means the pressure control means controlling a differential pressure using counterbalance valves
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- 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
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- 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
- F15B2211/575—Pilot pressure control
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- 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
- F15B2211/63—Electronic controllers
- F15B2211/6303—Electronic controllers using input signals
- F15B2211/633—Electronic controllers using input signals representing a state of the prime mover, e.g. torque or rotational speed
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- 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
- F15B2211/665—Methods of control using electronic components
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- 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
- F15B2211/7058—Rotary output members
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- 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
- F15B2211/763—Control of torque of the output member by means of a variable capacity motor, i.e. by a secondary control on the motor
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H59/00—Control inputs to control units of change-speed-, or reversing-gearings for conveying rotary motion
- F16H59/68—Inputs being a function of gearing status
- F16H2059/6838—Sensing gearing status of hydrostatic transmissions
- F16H2059/6876—Sensing gearing status of hydrostatic transmissions the motor speed
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
A hydraulic drive having a brake valve is disclosed, wherein the pressure acting on the brake valve in the opening direction is limited via a pressure-limiting valve. The latter can be set, for example, in dependence on the rotational speed or else can be set to a predetermined pressure.
Description
The present invention relates to a kind of fluid pressure drive device as described in the preamble according to claim 1.
By the known a kind of such fluid pressure drive device for capstan winch of DE10320946B4, wherein barrel of captan is driven by oil hydraulic motor.The feed line (entrance) of oil hydraulic motor and pump, preferably regulate pump to connect.The pressure medium flowed out from oil hydraulic motor flows to tank T via backflow.When there being tractive load to act on barrel of captan, barrel of captan may so be accelerated when braking not enough, namely be not enough to supply enough pressure mediums to oil hydraulic motor by the pressure medium volume flow of transport pump, the pressure drop therefore correspondingly in feed line and even may cause cavitation in feed line in adverse conditions.
In order to avoid undesirable pressure this in feed line reduces, in the solution known by DE10320946B4, brake valve is set, also referred to as the heavy brake valve that falls, it by pre-tensioner in closed position and in the direction of the opening by the pressure-loaded in corresponding feed line.In this known solution, design this brake valve in this wise, namely it is in two sense of rotation of oil hydraulic motor, that is works in the inflow replaced with during flowing back to.Pressure in feed line is enough large, brake valve is brought on an open position, thus flows out towards tank direction from the pressure medium volume flow that oil hydraulic motor flows out via brake valve.The pressure medium volume flow flowed out on tank direction in undesirable pressure reduction situation is by throttling or be blocked, and therefore oil hydraulic motor is correspondingly braked and pressure in feed line raises until brake valve is opened again.
In the solution that these are known, especially when the corresponding larger capacity of long feed line and input pipeline, appear at the pressure change in feed line (entrance) and therefore occur the corresponding fluctuation of the capacity of pressure surge and flexible pipe, thus brake valve correspondingly opens and closes due to this pressure surge, therefore the speed of oil hydraulic motor correspondingly fluctuates and is therefore difficult to realize the controlled motion of load.This vibration characteristics of oil hydraulic motor also can occur when pump has fault.
A kind of fluid pressure drive device fall with heavy brake valve is described in the DE102008064064A1 of claimant, wherein, this brake valve is loaded control signal in the direction of the opening, and this control signal intercepts on directional control valve, is controlled the conveying of the pressure medium of liquid in-out pressure motor by it.That is, in this flexible program, pressure medium is not directly depend on feed line pressure to the supply of oil hydraulic motor, therefore improves the vibration characteristics in above-mentioned special circumstances.But what have display is that the problems referred to above also there will be in this control situation of brake valve.
Correspondingly, therefore object of the present invention is to provide a kind of fluid pressure drive device, wherein prevents or at least reduces because the pressure in feed line (entrance) changes the speed oscillation caused.
This object is realized by a kind of fluid pressure drive device with the feature of claim 1.
Favourable expansion scheme of the present invention is the content of dependent claims.
According to fluid pressure drive device of the present invention, there is oil hydraulic motor, its joint can be connected with pressure medium source and pressure medium sink by means of working line, and there is brake valve assembly, it is attached troops to a unit in two working lines, and the pressure medium volume flow therefore flowed out can in both rotational directions by throttling.Two control rooms acted in the direction of the opening or in the closing direction of the brake valve of brake valve assembly are connected with the inlet opening joint of selector valve assembly, the larger pressure in the pilot pressure that this selector valve component selection applies in control room.The delivery outlet of selector valve assembly is connected with pressure-limit valve according to the present invention, and therefore the manipulation of brake valve assembly is determined in the lump by the pressure adjusted on pressure-limit valve, and this pressure is lower than expected pilot pressure maximum under corresponding running state.This pilot pressure acts on brake valve usually in the direction of the opening, the pressure that this acts in the direction of the opening according to the present invention is reduced to the pressure in the adjustment of pressure-limit valve place, therefore under the intake line of length and the corresponding larger capacity situation of working line, also can reduce pressure surge and the corresponding fluctuation of speed.Especially, adjust pressure-limit valve in this wise, namely can not exceed a maximum (top) speed preset of oil hydraulic motor and correspondingly can prevent overspeed.
Pressure-limit valve is designed to adjustable in a particularly preferred embodiment.
This adjustment can pure electricity mode or carry out in the mode of electric hydraulic pressure.
In an alternative embodiment, the spring housing of pressure-limit valve is connected with the tank joint of pressure-limit valve in inside.In another embodiment, spring housing can be loaded the pilot pressure of a pressure limiting, in order to adjust the pressure that will limit.
A flexible program regulation of the present invention, lead in the pipeline in above-mentioned control room at two and respectively arrange a damper, wherein, pilot pressure intercepts between control room and damper.
In a simple especially embodiment implemented, selector valve assembly is selector valve.Alternatively, selector valve assembly also can be consisted of check valve assembly.
Overspeed can be avoided especially effectively, if fluid pressure drive device is designed to speed probe, by its detection motor rotary speed and its signal by control unit process, then corresponding control signal is sent to pressure-limit valve by control unit, in order to so to control the pressure that will limit, namely exceed or close to during maximum speed from oil hydraulic motor pressure medium volume flow out by throttling so that brake fluid pressure motor.
The preferred embodiments of the present invention are explained in detail below by means of accompanying drawing.
Shown in accompanying drawing:
Fig. 1 is the circuti diagram according to fluid pressure drive device of the present invention,
Fig. 2 is the zoomed-in view of the motor unit of the brake valve assembly of the fluid pressure drive device had according to Fig. 1,
Fig. 3 is the zoomed-in view of the pump unit of fluid pressure drive device according to Fig. 1,
Fig. 4 is the partial view of a modification of embodiment according to Fig. 1,
Fig. 5 is the partial view of another modification embodiment illustrated in fig. 1, and
Fig. 6 is the plotted curve for illustration of the braking characteristic according to fluid pressure drive device of the present invention.
Fluid pressure drive device shown in Fig. 1 such as can be applied to travel driving unit, capstan driving device and chain sprocket driving device.In basic principle, shown fluid pressure drive device is made up of motor unit 1 and pump unit 2, and they are via working line 4, and 6 are interconnected.Hydraulic capacity and pipe resistance reference character 8 according to the diagram of Fig. 1,10 indicate.
Fig. 2 illustrates the zoomed-in view of the motor unit 1 of Fig. 1.According to this view, motor unit has oil hydraulic motor 1, such as axial piston governor motor, and its cradle (Schwenkwiege) can regulate by regulating cylinder 14.Regulate the pressure chamber 16 of the bottom side of cylinder 14 to be supplied to via the controller 20 be placed on shell 18 and control oil.The doughnut 22 of piston rod side and the on the pressure side connection of the corresponding of oil hydraulic motor 12, therefore act on all the time herein and have system pressure and will cylinder 14 be regulated pre-tensioner on the direction of maximum discharge capacity (often turning liquid inlet volume).In this base position, the pressure chamber 16 of bottom side is connected with tank T via controller 20.Regulate the adjustment of cylinder 22 to be undertaken by the motor modulating valve 24 of regulator 20, wherein, be connected with pressure regulator valve 26 in motor modulating valve 24 downstream.The structure principle of this controller is known, therefore only explains the parts that the understanding of the present invention is important herein.Motor modulating valve 24 is designed to can the directional control valve of step-less adjustment (continuously regulate), wherein, input adapter P is respectively via a safety check 28,30, and these two safety check are opened on the direction towards motor modulating valve 24, with two working lines 4,6, connect, this working line, as described, be connected on two working joints of oil hydraulic motor 12.Be responsible for making working line 4 by two safety check 28,30 in parallel, pressure higher in the pressure in 6 is applied on the joint P of motor modulating valve 24.The tank joint T of motor modulating valve 24 is connected with described tank T, and delivery outlet joint A is connected with the input adapter P of pressure regulator valve 26.The adjustment of motor modulating valve 24 is carried out by means of ratio magnet 32, and this ratio magnet is such as controlled by operating handle or analog.In the pre-tensioned base position of spring, tank joint T is connected with delivery outlet joint A and joint P is closed.
Pressure regulator valve 26 is regulated in the direction of its position (a) by the base position illustrated from it by the pressure of the input adapter P of pump control valve 24.In the pre-tensioned base position of spring, the input adapter P of pressure regulator valve 26 is connected with delivery outlet joint B, the pressure chamber 16 of the bottom side of the latter itself and adjustment cylinder 22 is in and controls in oily connection, therefore regulates cylinder to be unloaded (Vg max) by tank T direction in the base position shown in motor modulating valve 24 and pressure regulator valve 26.
The reduction of angle of oscillation and therefore the control ratio magnet 32 that increases through of rotating speed realize, wherein, modulating valve 24 is conditioned in one direction, and the pressure medium connection in the direction in which between the compression fittings P and delivery outlet joint A of motor modulating valve 24 is controlled (being opened).First pressure regulator valve 26 is retained in its pre-tensioned base position of shown spring.Correspondingly, then via safety check 28,30 make control room be connected with the pressure chamber 16 of bottom side, working line 4, higher pressure in 6 acts in this working room, thus controls oil and to flow in this pressure chamber and to regulate cylinder 22 mobile out and correspondingly cradle regulates on the direction that discharge capacity (Vg min) reduces based on its difference in areas.This adjustment is performed until in the power of ratio magnet 32 and reaches equilibrium of forces by regulating between the power of the Regulation spring of the piston tensioning of cylinder.
Pressure via pressure regulator valve 26 regulates and superposes with this electric proportion adjustment.If make system pressure rise to a maximum value preset by the power of Regulation spring 34 by loading moment or by reducing motor angle of oscillation, this system pressure intercepts at the P place, inlet opening of motor modulating valve 24 and against the masterpiece of Regulation spring 34 for the regulating piston of pressure regulator valve 26, so the regulating piston of pressure regulator valve 26 is moved in one direction, pressure medium connects B in the direction in which, T is controlled (opening), thus correspondingly the pressure chamber 16 of bottom side on tank direction unloaded and therefore oil hydraulic motor turn round again.By this increase and the reduction of consequent pressure of discharge capacity, adjusting deviation is then reduced.Oil hydraulic motor 12 exports larger moment of torsion by increasing discharge capacity under the pressure that maintenance is identical.
At two working lines 4, pressure in 6 is respectively via secondary pressure-limit valve 36,38 restrictions, the latter respectively has check (return) function, and this function authorized pressure medium is being flowed towards the on high-tension side secondary pressure-limit valve now worked by the secondary pressure-limit valve of low-pressure side.
Shell 18 adds brake valve assembly 40 in addition.This brake valve assembly has the brake valve 42 of known structural type itself.Each and one of them working line 4,6 of two inlet opening joint P, P' connects, and wherein, respectively arrange safety check 46,48 in the downstream of this joint, this safety check is authorized pressure media flow on the direction towards oil hydraulic motor 12 only.
The delivery outlet joint A of brake valve 42 is connected to working line 4 via the pipeline of the branch with two outlet non-return valves 47,49,6 be positioned at safety check 46, on the section in 48 downstreams.This outlet non-return valve 47,49 only allows the pressure medium flow on the direction of corresponding working line 4,6.
In the pre-tensioned base position of the spring of brake valve 42 (see Fig. 2), joint P, P' and A are closed each other.Two of brake valve 42 control side and respectively connect to relevant working line 4 or 6 via a damper 50,52.As shown in the details 52 of lower left quarter in fig. 2, each damper 50,52 have two damping nozzles 54 in parallel, 56, wherein, a rear damping nozzle is connected to safety check 58 upstream, and this safety check allows the flowing from the control oil of this relevant damping nozzle 56 and blocks the flowing controlling oil in the opposite direction.Correspondingly, damping nozzle 54 to working towards the control oil flow on direction, corresponding control room, and damping nozzle 56 determine and damping from control room out control oil flow.
In addition as shown in Figure 2, in the upstream of the damping nozzle 54 become a mandarin in decision control room, a db-pipeline 60,62 (also see details 52) is respectively branched out.These two db-pipelines 60,62 lead to the inlet opening of selector valve 64.Its delivery outlet is connected with pressure limiting pipeline 66, and this pressure limiting pipeline is connected on the inlet opening of pressure-limit valve 68.In an illustrated embodiment, this pressure-limit valve 68 is implemented as and can regulates to electric ratio, and the pressure maximum that therefore will limit is adjustable.This adjustment is undertaken by the signal of control unit 70 according to speed probe 71, detects the rotating speed of oil hydraulic motor 12 and its signal is sent to control unit 70 by this speed probe.Via selector valve 64 the larger pilot pressure in the control room of brake valve 42 be directed to pressure-limit valve 68 and then can be limited in a maximum value by corresponding adjustment, therefore such as the maximum (top) speed of oil hydraulic motor 12 is not exceeded.
In normal operation, brake valve 42 is based at working line 4, and in 6, the pressure difference of effect is regulated in the direction of the opening.If the input of pressure medium is such as carried out carrying out via working line 4 with the output of pressure medium via working line 6, so brake valve 42 is conditioned on the direction of adjusted position (a), connects controlled from the P of brake valve 42 to A (being opened) at this adjusted position upward pressure medium.Then pressure medium can to flow and from its other working joint via the part being positioned at safety check 48 upstream of working line 4 and brake valve 42 with and then return via safety check 47 and flow to working line 4 and then flow towards tank T direction towards oil hydraulic motor 12 via working line 6.The rotating speed of oil hydraulic motor 12 is monitored continuously in the case.In order to this rotating speed is no more than a maximum (top) speed, at pressure-limit valve 68 place adjustment pressure, this pressure is lower than the applied pressure in normal operation of the equipped at outlet port at selector valve 64, namely the pressure acted in the direction of the opening on brake valve 42 is reduced, therefore correspondingly set up a retardation pressure at motor equipped at outlet port, it prevents oil hydraulic motor 12 overspeed rotation.By suitably adjusting pressure-limit valve 68, suitable retardation pressure can be adjusted according to corresponding operational situation simply thus, in order to prevent oil hydraulic motor 12 overspeed rotation.
In an illustrated embodiment, brake valve assembly 40 is implemented as in addition has brake empty air valve (brake application magnet valve) 72, it by spring by pre-tensioner on locked position of coupler and via working line 4, larger pressure in pressure in 6 can regulate on the direction of an open position, this pressure is also intercepted by selector valve 74, on this open position, this larger pressure is drawn towards braking joint Br, it is connected with mechanical braking element, then this braking member passes through working line 4 according to the position of brake empty air valve 72, higher pressure in 6 in pressure is thrown off braking engagement.Owing to being applied to working line 4, system pressure in 6 is usually with inconsistent for braking (electromagnetic braking) required pressure that ventilates, therefore be connected with brake-pressure reducer 76 in the downstream of brake empty air valve 72 in an illustrated embodiment, by it, retardation pressure be reduced to the retardation pressure that is applicable to mechanical braking.
The pressure medium supply of oil hydraulic motor 12 is implemented by the pump unit 2 shown in Fig. 3.This pump unit can be implemented in a different manner; It relates to a kind of axial piston and regulates pump unit in the particular embodiment, by prior art its basic structure known, therefore only describes herein to understand some required parts.
Pump unit 2 has axial piston and regulates pump 78, and its delivered volume flow is conditioned by regulating the angle of oscillation of cradle.This adjustment is carried out via adjustment cylinder 80, and its conditioning chamber is connected via the delivery outlet of nozzle with pump control valve 82.Pump control valve 82 be implemented as can electric proportion adjustment directional control valve and via ratio magnet 84, on the direction increasing angle of oscillation and via adjustable spring and the Regulation spring 86 that is arranged in juxtaposition, on the direction reducing angle of oscillation (minimum delivery amount) is loaded.In the pre-tensioned base position of shown spring, described delivery outlet joint A is connected with input adapter P, and the latter itself is in pressure medium with the delivery outlet joint of selector valve 88 and is connected.At the inlet opening place of this selector valve 88, effect has the pumping pressure in pump line road 90 and acts on the other hand on the one hand has braking to regulate pressure, and this braking regulates pressure such as to be during starts responsible for making adjustment pump 78 not have to be conditioned on the direction of its minimum delivery amount (Vg min) in alive ratio magnet 84 situation at equipment.Pressure larger in pressure acts on the joint P of modulating valve 82 thus.On the delivery outlet of selector valve 88, this is externally connected with pilot line, and this pilot line passes into the control room of readjustment cylinder 92 via another nozzle, and regulating piston 94 sinks in this readjustment cylinder, and this regulating piston is mechanically connected with regulating the cradle of pump 78.The adjustment movement of regulating piston 94 is delivered on Regulation spring 86 via coupling mechanisms (interlocking mechanism) 96, and this Regulation spring is supported on the one hand on this coupling mechanisms 96 and on the other hand and loads on the direction of shown base position the adjustment slide core of modulating valve 82.
Readjustment cylinder 92 regulating piston 94 itself also via spring by pre-tensioner in a base position, wherein, act on readjustment cylinder 92 and regulate the spring force on cylinder 80 to be design like this, namely regulating pump that be not energized, pre-tensioner on the direction of maximum delivery (Vg max) under the state that do not activated.Equipment start and operating pressure set up during (modulating valve 82 is in base position) now angle of oscillation be adjusted in minimum delivery amount, therefore along with control electric current increase, blowback forwards in larger quantity delivered.
The tank joint T of modulating valve 82 regulates with pressure or the joint A of pressure shut-off valve 98 is connected, and its tank joint T is connected with tank T, and compression fittings P is connected with the delivery outlet joint of selector valve 88.Pressure valve 98, is connected with tank at this base position upper connection A by pre-tensioner base position shown in it by Regulation spring.Correspondingly, the tank joint T of pump control valve 82 is also connected with tank T.The pressure regulator valve 98 that can regulate continuously so can be regulated by the pressure in pump line road 90, and namely its input adapter P is connected with the delivery outlet joint A of pressure regulator valve 98 and pumping pressure in this region works thus.In ratio magnet 84 situation be energized, regulate the control room of cylinder 80 to be controlled (closing) and control oil to be fed into the control room regulating cylinder 80 to the pressure medium joint of tank T, therefore this control cylinder shifts out and correspondingly regulates pump 78 toward back rotation.That is, when exceeding the design load of the Regulation spring via it at pressure regulator valve 98 place adjustment, pump is automatically reduced adjusting deviation toward back rotation.The adjustment of this pressure regulates with aforesaid EP-and superposes.
Regulate the suction joint of pump 78 to be connected on the compression fittings of suction booster 100, the pressure medium from tank T can be transported by this suction booster.The centrifugal pump that this suction booster 100 normally also works under higher rotation speed.Suction booster 100 especially makes to become easy with the cold starting under the corresponding high viscosity of pressure medium at low temperatures.
In an illustrated embodiment, same live axle yet has a supply pump 102, pressure medium can be transported to supply pipeline 103 from tank T by it.This supply pipeline leads to two outlet non-return valves 47, between 49 according to the diagram of Fig. 2.
The joint P of directional control valve 104 is led on pump line road 90.This direction is penalized and can be purely conditioned to electrically or with the mode of electric hydraulic pressure or other mode.Two working joint A, B is connected to working line 4, on 6.Tank joint T passes in tank T.Shown, such as, in the base position of the spring centering heart, two working joint A, B are connected with tank T via the mode of nozzle according to a kind of floating position.When regulating on direction " 2 ", compression fittings P is connected with working line 6 and tank joint T is connected with the working line 4 being now placed in outflow lines (outlet).When direction " 1 " upper adjustment directional control valve 104, in the opposite manner, joint P is connected with working joint B and tank joint T is connected with working joint A.As shown in phantom in Figure 3, directional control valve 104 also can so design, and namely pump line road is also connected with tank T by it in base position (0).When direction " 1 " or " 2 " upper adjustment directional control valve 104, this circulation position is closed.
Pressure in supply pipeline 103 can also limit via supply pressure-limit valve 106.
Pressure regulator valve 98 is also implemented as and has remote control system (remote control) 108 in an illustrated embodiment.It is made up of pressure-limit valve 110 and the control valve 112 being implemented as 2/2 directional control valve in principle, and they can use individually or in combination.Pressure-limit valve 110 is designed to be adjustable and in limiting pressure pilot line 114 pressure, and this pressure control conduit is connected with pump line road 90 via nozzle 116.Pressure in pressure control conduit 114 to act on pressure regulator valve 98 and therefore acts on side by side with its pressure regulating spring on the direction of the base position of pressure regulator valve 98.Therefore, by correspondingly adjusting the pressure at pressure-limit valve 110 place, the pilot pressure acted on the direction of the base position of pressure regulator valve 92 can be changed, therefore can adjust lower pressure design value (theoretical value) in a straightforward manner.
Pressure control conduit 114 can be made to unload on the direction of tank T by control valve 112, priming of pump can realize with low-down operating pressure (standby operating pressure) thus.This control valve 112 also may be embodied to can (stepless) directional control valve of regulating continuously.
Fig. 4 illustrates a kind of modification of previous embodiment, and wherein substituting can the pressure-limit valve 68 of electric proportion adjustment, and use a kind of special structure form, wherein spring housing is connected with the tank joint of pressure-limit valve 68 in inside.
At the adjustable pressure in pressure-limit valve 68 place, this pressure loads brake valve 42 on the direction of (relevant to sense of rotation) opening direction of brake valve 42, now must adjust at the spring place of pressure-limit valve 68, wherein, the back pressure of the part at the working line being placed in outlet must be considered.Based on regulate and can specify, the pressure that limit is approximately 40 bar and adds this back pressure.Limited the spool upward pressure acting on brake valve 42 in the direction of the opening thus by pressure-limit valve 68, therefore its lift also keeps constant under the system pressure conditions increased.
In embodiment in Figure 5, the Flow characteristics line (supply characteristics line) of two safety check 47,49 is used by as measuring diaphragm.The flow resistance relevant to particular device is by reverse selector valve 118 and compensated by the pilot pressure of effect in pilot line 116 thus, and in fact the change therefore on equipment does not affect, and this change is to the flow passage resistance generation effect of return line.
Fig. 5 illustrates another kind of modification, wherein pressure-limit valve 68 is loaded by the changeable power of pressure limiting spring on the one hand and in the closing direction additionally by the pressure-loaded in pilot line 116, this pilot line is connected on the delivery outlet joint A of reverse selector valve 118, two inlet opening joint P of this selector valve, P' is each with a working line 4,6 connect, and wherein, in pressure, each lower pressure is continued to be directed to joint A.
In shown embodiment, two pressure limiting pipelines 60,62 are interconnected via supply safety check 120,122, and wherein, supply pipeline 103 is passed at two supply safety check 120, in the region between 122.Also conventional pressure-limit valve can be used in principle to substitute particular valve structure pattern in Figure 4 and 5.
As already described, brake valve 42 1 aspect is by working line 4, pressure difference in 6, exactly be conditioned in the direction of the opening by the too much pressure (superpressure) in the working line guiding higher pressure and by the back pressure in corresponding outlet (outflow lines), wherein, according to the situation of opening cross-section, the pressure medium volume flow flowed out from oil hydraulic motor 12 and these power difference/pressure difference are pro rata by throttling.Detect the rotating speed of oil hydraulic motor 12 by speed probe 71 and control pressure-limit valve 68 (at the circuit according to Fig. 2) when reaching storage maximum speed in a control unit or maximum speed scope, so to adjust the pressure that will limit, namely act on the pressure on brake valve 42 to be in the direction of the opening lowered relative to the pressure (in pressure-limit valve 68 situation of closing) of practical function, therefore due to the opening cross-section of the press-brake valve 42 reduced in the direction of the opening is reduced and the pressure medium volume flow correspondingly flowed out by throttling.This characteristic can describe very intuitively by means of the plotted curve in Fig. 6.The figure illustrates a plotted curve, illustrated therein is the pressure of the motor equipped at outlet port according to rotating speed, namely produce the pressure of braking moment.Pressure-limit valve is adjusted to the pressure maximum of roughly 70 bar (bar) according to previous embodiment in this embodiment, and maximum (top) speed should be about 1800 turns.
Seeing according in the diagram of Fig. 6, the pressure under the rotating speed reduced in scope between 20bar and 40bar acts on motor delivery outlet clear enough, and this pressure easily raises along with the rotating speed increased.In higher speed range, now general proportions too greatly (disproportionately) rising of pressure in outflow lines (outlet), reaching after the threshold value (threshold value) of pressure-limit valve place adjustment or after controlling (opening) pressure-limit valve according to rotating speed (embodiment according to Fig. 2), the pressure of outlet side then raises strongly, wherein, rotating speed now then no longer exceedes the value of 1800 turns that adjust in advance, because motor is braked by the braking moment acted on it in an efficient way.Motor rotary speed now keeps in this range by pressure-limit valve 68, and wherein, the fluctuation of speed is minimum, and therefore in fact the hypervelocity of motor can not occur.The pressure change measurable, relevant to rotating speed at motor inlet opening place is positioned at above the curve shown in Fig. 6 naturally, but has roughly the same feature.
Disclose a kind of fluid pressure drive device with brake valve, wherein, the pressure acted in the direction of the opening on brake valve is limited by pressure-limit valve.This pressure-limit valve such as can carry out adjusting or can be adjusted on a predetermined pressure according to rotating speed.
Claims (9)
1. fluid pressure drive device, there is oil hydraulic motor (12), the joint of oil hydraulic motor is by means of working line (4, 6) be connected with pressure medium source and pressure medium sink, and have and two working lines (4, 6) arrange, the brake valve assembly (40) hydraulically manipulated, can the pressure medium volume flow that flows out from oil hydraulic motor (12) of throttling by this brake valve assembly, it is characterized in that, two control rooms of brake valve (42) are hydraulically connected with selector valve assembly, pilot pressure larger in the pilot pressure of this selector valve component selection in control room, thus corresponding control room is connected with pressure-limit valve (68).
2. drive unit according to claim 1, wherein, it is adjustable that pressure-limit valve (68) is implemented as.
3. drive unit according to claim 1 and 2, wherein, pressure-limit valve (68) is implemented as and can electric mode regulates.
4. according to drive unit in any one of the preceding claims wherein, wherein, the spring housing of pressure-limit valve (68) is connected with a tank joint (T) in inside.
5. drive unit according to any one of claim 1 to 3, wherein, the spring housing of pressure-limit valve (68) can load with pilot pressure.
6. drive unit according to claim 5, wherein, described pilot pressure is pressure less in the pressure in feed line and in outflow lines, and this pressure intercepts via a reverse reversing valve assembly.
7. according to drive unit in any one of the preceding claims wherein, wherein, in the pilot line in each control room leading to brake valve (42), a damper (50 is respectively set, 52) and between corresponding control room and described damper (50,52), carry out the intercepting of pilot pressure.
8. according to drive unit in any one of the preceding claims wherein, wherein, selection mechanism is selector valve (64) or check valve assembly.
9., according to drive unit in any one of the preceding claims wherein, there is the speed probe (71) for detecting motor rotary speed and the control unit (70) for controlling pressure-limit valve (78) according to tach signal.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102012012977.7 | 2012-06-29 | ||
| DE102012012977.7A DE102012012977B4 (en) | 2012-06-29 | 2012-06-29 | Hydraulic drive |
| PCT/EP2013/061564 WO2014001043A1 (en) | 2012-06-29 | 2013-06-05 | Hydraulic drive |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN104379972A true CN104379972A (en) | 2015-02-25 |
| CN104379972B CN104379972B (en) | 2016-09-28 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201380034063.2A Active CN104379972B (en) | 2012-06-29 | 2013-06-05 | Fluid pressure drive device |
Country Status (3)
| Country | Link |
|---|---|
| CN (1) | CN104379972B (en) |
| DE (1) | DE102012012977B4 (en) |
| WO (1) | WO2014001043A1 (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105485072A (en) * | 2015-12-07 | 2016-04-13 | 北京航空航天大学 | Cabin door transient actuating device and system based on secondary regulation and control method |
| CN106015503A (en) * | 2015-03-24 | 2016-10-12 | 福特全球技术公司 | Transmission Hydraulic Control System |
| CN106246620A (en) * | 2015-06-09 | 2016-12-21 | 罗伯特·博世有限公司 | Control block, with the hydrostatic driving means controlling block and the method being used for the vehicle with hydrostatic driving means |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102020208594B4 (en) * | 2020-07-09 | 2023-02-09 | Robert Bosch Gesellschaft mit beschränkter Haftung | Hydrostatic auxiliary drive |
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- 2012-06-29 DE DE102012012977.7A patent/DE102012012977B4/en active Active
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2013
- 2013-06-05 CN CN201380034063.2A patent/CN104379972B/en active Active
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| DE4329689C1 (en) * | 1993-09-02 | 1995-02-23 | Hydromatik Gmbh | Control device for a hydrostatic transmission |
| EP0957210A1 (en) * | 1998-05-13 | 1999-11-17 | Poclain Hydraulics Industrie | Hydraulic circuit with hydraulic motor and a three-position-valve |
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| CN106015503A (en) * | 2015-03-24 | 2016-10-12 | 福特全球技术公司 | Transmission Hydraulic Control System |
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| CN106246620A (en) * | 2015-06-09 | 2016-12-21 | 罗伯特·博世有限公司 | Control block, with the hydrostatic driving means controlling block and the method being used for the vehicle with hydrostatic driving means |
| CN105485072A (en) * | 2015-12-07 | 2016-04-13 | 北京航空航天大学 | Cabin door transient actuating device and system based on secondary regulation and control method |
| CN105485072B (en) * | 2015-12-07 | 2017-08-25 | 北京航空航天大学 | Hatch door transient state acting device, system and control method based on Secondary Control |
Also Published As
| Publication number | Publication date |
|---|---|
| WO2014001043A1 (en) | 2014-01-03 |
| DE102012012977A1 (en) | 2014-04-17 |
| CN104379972B (en) | 2016-09-28 |
| DE102012012977B4 (en) | 2023-06-07 |
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