CN102878127A - Hydrostatic drive system - Google Patents
Hydrostatic drive system Download PDFInfo
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- CN102878127A CN102878127A CN2012102438435A CN201210243843A CN102878127A CN 102878127 A CN102878127 A CN 102878127A CN 2012102438435 A CN2012102438435 A CN 2012102438435A CN 201210243843 A CN201210243843 A CN 201210243843A CN 102878127 A CN102878127 A CN 102878127A
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- reset signal
- volume flow
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- pump
- 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
- 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
- F15B11/05—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed specially adapted to maintain constant speed, e.g. pressure-compensated, load-responsive
- F15B11/055—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed specially adapted to maintain constant speed, e.g. pressure-compensated, load-responsive by adjusting the pump output or bypass
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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
- 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
- F16H61/42—Control of exclusively fluid gearing hydrostatic involving adjustment of a pump or motor with adjustable output or capacity
- F16H61/433—Pump capacity control by fluid pressure control means
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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
- F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
- F15B2211/205—Systems with pumps
- F15B2211/2053—Type of pump
- F15B2211/20546—Type of pump variable capacity
- F15B2211/20553—Type of pump variable capacity with pilot circuit, e.g. for controlling a swash plate
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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
- F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
- F15B2211/255—Flow control functions
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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
- F15B2211/30—Directional control
- F15B2211/31—Directional control characterised by the positions of the valve element
- F15B2211/3105—Neutral or centre positions
- F15B2211/3111—Neutral or centre positions the pump port being closed in the centre position, e.g. so-called closed centre
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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
- F15B2211/30—Directional control
- F15B2211/31—Directional control characterised by the positions of the valve element
- F15B2211/3144—Directional control characterised by the positions of the valve element the positions being continuously variable, e.g. as realised by proportional 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
- F15B2211/60—Circuit components or control therefor
- F15B2211/63—Electronic controllers
- F15B2211/6303—Electronic controllers using input signals
- F15B2211/6336—Electronic controllers using input signals representing a state of the output member, e.g. position, speed or acceleration
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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
- F15B2211/6346—Electronic controllers using input signals representing a state of input means, e.g. joystick position
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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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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Fluid-Pressure Circuits (AREA)
- Control Of Positive-Displacement Pumps (AREA)
Abstract
本发明涉及一种静液压驱动系统(1)，具有一输送体积流量可调的泵(2)，所述泵被设置用于对至少一个消耗器(V)进行供给，泵(2)的输送体积流量调节装置(10)借助于预给定信号朝增高输送体积流量的方向控制并且根据一检测所述泵(2)的被过量输送的体积流的液压复位信号朝降低输送体积流量的方向控制，为了产生所述复位信号设置一循环压力天平(31)，所述循环压力天平在一复位信号产生位置(31b)中产生所述液压复位信号。根据本发明，给引导所述液压复位信号的复位信号管路(32)配置压力限制装置(50)和/或设置一用于液压复位信号的关断装置(70)。
The invention relates to a hydrostatic drive system (1) having a pump (2) with an adjustable delivery volume flow, which is provided for supplying at least one consumer (V), the pump (2) delivering The volume flow regulator (10) is controlled with the aid of a preset signal in the direction of increasing the delivery volume flow and in response to a hydraulic reset signal which detects the overdelivered volume flow of the pump (2) in the direction of decreasing the delivery volume flow , in order to generate the reset signal, a cyclic pressure balance (31) is provided, and the cyclic pressure balance generates the hydraulic reset signal in a reset signal generating position (31b). According to the invention, the reset signal line ( 32 ) carrying the hydraulic reset signal is assigned a pressure limiting device ( 50 ) and/or a shut-off device ( 70 ) for the hydraulic reset signal is provided.
Description
Technical field
The present invention relates to a kind of hydrostatic drive system, has the adjustable pump of a delivered volume flow, described pump is arranged for to be supplied with at least one customer, wherein, the delivered volume flow regulator of described pump loads and loads towards the direction that reduces the delivered volume flow according to the hydraulic reposition signal of the volume flow of an excessive conveying that detects described pump towards the direction that increases the delivered volume flow by means of predetermined signal, wherein, in order to produce described reset signal, one circulating pressure balance is set, and described circulating pressure balance produces in a reset signal and produces described hydraulic reposition signal in the position.
Background technique
In this drive system, the delivered volume flow of pump is adjusted on the desired volume flowrate demand of controlled customer, thus described customer can be with movement velocity predetermined on control valve in the situation that energy loss is little works.This drive system is used for control hydraulic consumers device in mobile operation machinery, for example excavator or floor delivery tool.
In known load-transducing formula drive system, pump is with the open cycle loop works and corresponding control valve is set controls customer, in described load-transducing formula drive system, the delivered volume flow of pump is regulated by highest load pressure and the adjustment pressure reduction of controlled customer.When the one or more control valve of control, on control valve, adjust respectively definite open cross-section.Described pump is regulated towards the direction that increases the delivered volume flow so for a long time by the highest load pressure of the setting of controlled customer, until the discharge pressure of pump is higher than the highest load pressure of controlled customer with described adjustment pressure reduction.What realize thus is that the desired volume flow demand of the respective openings cross section that passes through control valve of controlled customer is provided by described pump.
But because being highest load pressure according to controlled customer, the adjustment of pump delivered volume flow carries out, therefore cause pump the adjustment of delivered volume flow time lag response characteristic and cause thus beginning by the motion that adjusts of controlling motion that corresponding control valve introduces and customer between appreciable time lag because control the only just generation after control valve is loaded in the open position of induced pressure of described pump.This is operated the low-power that personnel are considered as drive system.
For fear of described shortcoming, in the drive system of described type, controlled towards the direction that increases the delivered volume flow by the delivered volume flow regulator of the predetermined signal adjusting pump that quantity delivered is adjustable.One hydraulic reposition signal is used for the quantity delivered of described pump is adjusted to the desired conveying stream of controlled customer demand, and described hydraulic reposition signal loads described delivered volume flow regulator towards the direction that reduces the delivered volume flow.In order to produce described hydraulic reposition signal, a circulating pressure balance by the induced pressure control of the discharge pressure of pump and customer is set, this circulating pressure balance is at the control seamed edge or adjust seamed edge and produce the hydraulic reposition signal.This circulating pressure balance can be arranged in the branch line that delivery line and container are coupled together at this, wherein, produce in the position a reset signal that is configured to through-flow position, arrange in described branch line at one to produce a speed in the described circulating pressure balance throttling arrangement downstream, that be configured to Venturi tube to hold up masterpiece be the hydraulic reposition signal.
The drive system of described type is disclosed by DE102008038381A1 and DE102008038382A1.In DE102008038381A1, pump can electronics-and hydraulically controlled or adjustable aspect the input volume flowrate.The hydraulic reposition signal loads the delivered volume flow regulator towards the direction that reduces the delivered volume flow, this hydraulic reposition signal a circulating pressure balance (described circulating pressure balance is arranged in the branch line that delivery line and a container of described pump are coupled together) upper with one in described circulating pressure balance arranged downstream in branch line and be configured to produce in the throttling arrangement of Venturi tube.
In order to control the quantity delivered of described pump, arrange one and regulate the pressure valve device in DE102008038381A1, the loading that pressure is controlled the regulating piston device that is connected with the delivered volume flow regulator formation effect of described pump is regulated in this adjusting pressure valve device utilization.Described adjusting pressure valve device construction be can be automatically controlled reduction valve, its for the quantity delivered that improves described pump can be by consisting of predetermined signal electric control signal towards reduce the direction to control of regulating pressure and by the hydraulic reposition signal resist described electric control signal towards improve regulate pressure direction to control to reduce the quantity delivered of described pump.By the adjusting pressure that is produced by described adjusting pressure valve device, described adjusting pressure valve device is loaded towards the direction that reduces the delivered volume flow, in order to the quantity delivered of pump is adjusted on the desired feed flow demand of customer.
Do not need the adjusting pressure valve for the delivered volume flow regulator of control pump in DE102008038382A1, in the document, the control of the delivered volume flow of pump or adjustment are carried out in the mechanical-hydraulic mode.The regulating piston device that is connected with the input volume flowrate controlling mechanism formation effect of pump is loaded towards the direction that improves the delivered volume flow as predetermined signal by hydraulic regulation pressure or spring constantly at this.Described regulating piston device is loaded towards the direction that reduces quantity delivered by the hydraulic reposition signal.
In the drive system of described type, use following pump, the quantity delivered of described pump is adjusted the mode difference and thereby quantity delivered is adjusted the control mode difference of control valve unit and used different controlling devices for the quantity delivered of regulating pump, for example in DE102008038381A1, adopt electronics-hydraulic pressure adjustment or in DE102008038382A1, adopt the mechanical-hydraulic adjustment, wherein, use different adjusting stress levels.At this, for the high coordination of adaptive described hydraulic reposition signal demand expends.
In addition, in specific running state, the minimizing of the pump duty that is caused by the hydraulic reposition signal is not expected.This running state will appear when operator change with the quick and multiple speed of customer when providing in advance ballistic kick formula or the motion of vibrating type customer for example.The hydraulic reposition signal exceeded customer demand, testing pump excessive conveying volume flow and cause that the reduction of pump duty passes through, by described hydraulic reposition signal, thereby in the situation that this customer motion cause the customer motion reduction power performance and cause the low-power performance of drive system.
Summary of the invention
Task of the present invention is, the hydrostatic drive system that provides a kind of this paper to start described type, and it has avoided the shortcoming mentioned.
According to the present invention, described task solves in the following manner, that is, give the reset signal pipeline configuration pressure limit device of the described hydraulic reposition signal of guiding and/or a cutoff device for the hydraulic reposition signal is set.
Utilize configuration can limit the height of described hydraulic reposition signal and make it suitable with the adjusting stress level of the selected control gear of delivered volume flow regulator in simple mode to the pressure limit device of reset signal pipeline.Can make the stress level of control gear of the stress level of hydraulic reposition signal and delivered volume flow regulator suitable in simple mode thus, thereby in the different control programs of proportioner with have in the situation of different schemes of controlling device of different adjustment stress level and allow simply and flexibly to adopt quantity delivered control of the present invention.
Utilize the cutoff device for the hydraulic reposition signal of the present invention to make the hydraulic reposition signal (it causes the reduction of the delivered volume flow of pump) that produces at the circulating pressure balance in simple mode thus interrupt and avoid the quantity delivered that described hydraulic reposition signal causes of passing through of pump to reduce.Thus, thus utilize this cutoff device to avoid the reduction of not expecting of pump duty and in specific running state, to realize controlled customer and power that realize the improvement of drive system in simple mode by turn-offing described hydraulic reposition signal for the chatter on the motion of specific customer, for example customer.
Preferred embodiment particularly preferably be according to one of the present invention, cutoff device is made of shut-off valve, and described shut-off valve is arranged in the reset signal pipeline of the described hydraulic reposition signal of a guiding.Utilize shut-off valve in the reset signal pipeline to make the hydraulic reposition signal (it causes the reduction of the delivered volume flow of pump) that produces at the circulating pressure balance in simple mode thus interrupt and avoid the quantity delivered of pump to reduce by described hydraulic reposition signal.
The advantage that obtains in simple configuration aspects is, described shut-off valve has on positi and scram position, and in described on positi, the reset signal pipeline that leads to the delivered volume flow regulator is opened, in described scram position, described reset signal pipeline is cut off.Utilize this two-position valve, for example changing valve simple in structure can allow in simple mode the quantity delivered that turns on and off to control described pump of hydraulic reposition signal.
If in the branch that leads to the delivered volume flow regulator of reset signal pipeline described in the scram position of described shut-off valve towards a container off-load, then can realize that controlling device is by the off-load of hydraulic reposition signal in simple mode, thereby can determine the predetermined signal of described quantity delivered for regulating pump, carry stream so that described pump loads and provides corresponding to presetting of described predetermined signal towards the direction that improves the delivered volume flow thus.
What meet the purpose requirement is that described shut-off valve can be changed between on positi and scram position by means of a control device, particularly magnetic switch.Described shut-off valve can or directly be controlled in electric mode with hydraulic way, electronics-hydraulic way at this.Described shut-off valve is controlled permission simply and is controlled inexpensively described shut-off valve by the direct electricity that magnetic switch realizes.
According to a further scheme of the present invention, described reset signal pipeline by means of a Venturi tube towards a container off-load.Utilize this Venturi tube that one volume flow is flowed out towards container from the reset signal pipeline, wherein, thus by selecting Venturi tube to change and regulating the described volume flow that flows out towards container and the pressure gradient that can affect the hydraulic reposition signal that occurs in the reset signal pipeline.
Particularly advantageous is that to predetermined delivered volume flow, particularly preconditioning is to very big delivered volume flow by means of the predetermined signal preconditioning that occurs in a signal pipeline for described pump.Thus, by a corresponding constant or variable predetermined signal, with described pump by described predetermined Signal Regulation to the delivered volume flow of determining, particularly be adjusted on the very big delivered volume flow, thus, described pump provides predetermined feed flow, and very big feed flow preferably is provided.If the conveying stream that is provided by pump is not provided customer fully, then produce a hydraulic reposition signal at the circulating pressure balance, thus, the quantity delivered by reducing described pump so that the delivered volume flow adaptation of described pump in the demand of customer and restriction or reduce and be not consumed the excess volume stream that device receives.
If described pump by means of the predetermined signal preconditioning that occurs in the signal pipeline to predetermined feed flow, then when described predetermined signal can by means of a predetermined valve, particularly can electricity regulate Signal Regulation the time obtain special advantage.Thus, consist of the volume flow restriction of the predetermined value of volume flow and formation pump by the delivered volume stream of described predetermined signal sets.Thus, can change and regulate the volume flow restriction of described pump and for example make it suitable with the driving power of the driving machine that drives described pump in simple mode by changing and regulating described predetermined signal.
Description of drawings
The below elaborates additional advantage of the present invention and details by means of the embodiment shown in the schematic diagram.In the accompanying drawing:
Fig. 1 is the circuti diagram of the first mode of execution of hydrostatic drive of the present invention system,
Fig. 2 is the circuti diagram of the second mode of execution of hydrostatic drive of the present invention system,
Fig. 3 is the circuti diagram of the 3rd mode of execution of hydrostatic drive of the present invention system.
Embodiment
The circuti diagram of the drive system 1 that a load-transducing of the present invention shown in Figure 1 is regulated.This drive system 1 is for example used in mobile operation machinery, preferred excavator or floor delivery tool.
This drive system 1 has the adjustable pump of delivered volume flow 2, and described pump forms to drive with the open circuit operation and with driving machine 3, for example internal-combustion engine and is connected to drive.Described pump 2 is connected with container 5 by means of pipeline 4 and pressure medium is transported in the delivery line 6 in the suction side.
In order to control one or more customer V, a control valve 7 is set respectively, described control valve is configured to the directional control valve in the neutral position throttling.
Described control valve 7 is connected to described delivery line 6, a container pipeline 9 and some are on pressure medium pipeline 8a, the 8b of customer V.When handling control valve 7, pressure medium pipeline 8a, the 8b that control valve 7 control in corresponding control position 7a, 7b is described leads to customer V and described delivery line 6 are connected with the container pipeline be connected and according to pilot line 7c, 7d in the certain openings cross section of control signal release from delivery line 6 to pressure medium pipeline 8a or 8b that occur.Give the control valve pressure balance that is used for irrespectively controlling with induced pressure the movement velocity of described customer 6 that 7 configurations are not shown specifically.
In order to control described control valve 7, an electric control device 80 is set, described electric control device input side and predetermined device 81 for example operating handle formation effect be connected.In order to control described control valve 7, this control valve has for example magnet of corresponding electric control device, and described control device is connected with control gear 80 at outlet side.Replace electric control device ground, also can load described control valve 7 with hydraulic way, wherein, but the pilot pressure valve of electric control can be set in order to produce the pilot pressure that loads described control valve 7, described pilot pressure valve is connected with described control gear 80 at outlet side.
Described pump 2 is configured to the adjustable pump of quantity delivered, and its delivered volume flow can be regulated by means of delivered volume flow regulator 10.For this reason, one regulating piston device 11 is set, described regulating piston device has and is arranged in the regulating piston 13 of regulating in the cylinder 12, and delivered volume flow control device, for example pitch mode of structure of described regulating piston and described delivered volume flow regulator 10 and the adjustable pitch formation effect of slope that is configured to the axial flow reciprocating pump are connected.
Regulating piston device 11 has the pressure chamber 14 of adjusting, and described adjusting pressure chamber loads the direction of delivered volume flow regulator 10 towards very big delivered volume flow.Regulating piston device 11 has an other adjusting pressure chamber 15, and described other adjusting pressure chamber loads the direction of delivered volume flow regulator 10 towards minimum delivered volume flow.Described regulating piston 13 can load towards the direction of very big delivered volume flow by means of the spring F that is arranged in the described adjusting pressure chamber 14.Described regulating piston 13 can be loaded by the direction of the adjusting pressure that exists in the pilot pressure chamber 15 of described regulating piston device 11 towards minimum delivered volume flow.
Delivered volume flow regulator 10 in the accompanying drawing can be controlled in the mode of electronics-hydraulic pressure.For this reason, adjusting pressure valve 20, for example reduction valve that can electric control is set in regulating pressure piping 16.Described adjusting pressure valve 20 is connected with pilot pressure source 18, for example feeding pump or the pilot pressure pump of described drive system 1 at input side.But also passable is that described adjusting pressure valve 20 is connected on the delivery line 6 of described pump at input side.The pilot pressure chamber 14 that is provided with spring F of described regulating piston device 11 is towards described container 5 off-loads.
In addition, described control gear 80 is connected with described adjusting pressure valve 20 at outlet side, but described adjusting pressure valve is configured to the adjusting pressure valve of electric control.Electric control device 80 consists of at this corresponding control gear by adjusting control valve 20, wherein, produces the corresponding pressure of regulating in regulating pressure piping 16.Thereby a predetermined device is for example controlled the delivered volume flow regulator 10 of pump the control signal of described control valve 7 and is controlled the control signal of customer V towards the direction loading of raising delivered volume flow according to being used for according to being used for, thereby so that pump 2 provides one by the control gear of described adjusting pressure valve 20 predetermined quantity delivered and a conveying stream that presets.
One hydraulic reposition input is by pump 2 excessive conveyings and surpass the volume flow of customer V demand, and pump 2 is loaded towards the direction that reduces the delivered volume flow by described hydraulic reposition signal.In order to produce described hydraulic reposition signal, at one a circulating pressure balance 31 is set from the branch line 30 that delivery line 6 branches out, wherein, described circulating pressure balance 31 is connected on the branch line 30 and is connected at outlet side on the reset signal pipeline 32 of a described hydraulic reposition signal of guiding at input side.
Described circulating pressure balance 31 has the rest position 31a and the through-flow position that branch line 30 is connected with reset signal pipeline 32 that are connected cut-off that makes branch line 30 and reset signal pipeline 32, described through-flow position formation reset signal generation position 31b.Described circulating pressure balance 31 is loaded and is loaded towards the direction that reset signal produces position 31b by the discharge pressure of pump 2 towards the direction of rest position 31a by the highest load pressure of controlled customer V and spring assembly 33.For this reason, the induced pressure notice pipeline 34 of the highest load pressure of a controlled customer V of guiding be connected to described circulating pressure balance 31 on the chain of command of the directive effect of rest position 31a.Pilot line 35 that branches out from described delivery line 6 or branch line 30 is connected to producing on the chain of command of directive effect of position 31b towards reset signal of described circulating pressure balance 31.Described circulating pressure balance 31 preferable configuration are the control valve in the neutral position throttling.
In the situation of the delivered volume flow regulator 10 of Fig. 1, the reset signal pipeline 32 of guiding hydraulic reposition signal leads on the adjusting pressure valve 20 of this delivered volume flow regulator 10 to load this adjusting pressure valve.Described hydraulic reposition signal reacts on described electric control signal and causes the rising of regulating the adjusting pressure in the pressure piping 16 in described adjusting pressure valve, thus, delivered volume flow regulator 10 antagonistic spring F are in order to reduce delivered volume flow being adjusted on the controlled customer 7 desired volume flow demands towards the direction loading of minimum delivered volume flow and the delivered volume flow of described pump 2 by the volume flow of excessive conveying according to pump.Therefore, according to described hydraulic reposition signal, delivered volume flow regulator 10 is controlled towards the direction of the quantity delivered that reduces pump 2, in order to will be adjusted on the desired demand of controlled customer V by the conveying stream that pump 2 is carried.
Described reset signal pipeline 32 can be by means of Venturi tube (Staud ü se) 60 towards container 5 off-loads.Described Venturi tube, for example orifice plate are arranged in one and lead to the branch line 61 of container 5 from described reset signal pipeline 32.Utilize described Venturi tube 60 can affect by the volume flows of 5 outflows from described reset signal pipeline 32 towards container the pressure gradient of the hydraulic reposition signal that produce.
In the situation of the drive system 1 of Fig. 1, according to the present invention, give the reset signal pipeline that leads to delivered volume flow regulator 10 32 configuration pressure limit devices 50, utilize described pressure limit device can limit and be adjusted in case of necessity the height of the hydraulic reposition signal of reset signal pipeline 32 guiding.Pressure limit device 50 is configured to the pressure limit valve, and it is arranged in one and branches out and lead to the branch line 51 of container 5 from reset signal pipeline 32.
In addition, in Fig. 1, according to the present invention, a cutoff device 70 that is used for the hydraulic reposition signal that the described quantity delivered that causes pump 2 reduces is set.
In an illustrated embodiment, cutoff device 70 consists of by being arranged in the shut-off valve 71 that leads in the reset signal pipeline 32 of regulating pressure valve 20, and it has on positi 71a, and in described on positi, reset signal pipeline 32 is opened.Described shut-off valve 71 also has scram position 71b, and in described scram position, described reset signal pipeline 32 is cut off.Thereby in order in scram position 71b, to realize the off-load of described adjusting control valve by the hydraulic reposition signal and to realize the shutoff that quantity delivered that the hydraulic reposition signal causes reduces of passing through of pump 2, shut-off valve 71 is connected on the off-load pipeline 72 of container 5, wherein, in scram position 71b, the branch that lead to regulate pressure valve 20 of reset signal pipeline 32 is connected with described off-load pipeline 72 and thus towards container 5 off-loads.In addition, in scram position 71b, the branch from the circulating pressure balance of reset signal pipeline 32 is cut off.In on positi 71a, off-load pipeline 72 is cut off.
In an illustrated embodiment, shut-off valve 71 is configured to changing valve.Shut-off valve 71 can be controlled between on positi 71a and scram position 71b by means of control device 75.In an illustrated embodiment, shut-off valve 71 can be controlled by electricity, wherein, a magnetic switch is set as control device 75.Described control device 75 is connected with described control gear 80 formation effects in order to control preferably.
The pressure limit device 50 of Fig. 1 is arranged in cutoff device 70 downstreams and so is arranged between cutoff device 70 and the adjusting pressure valve 20.
The second mode of execution of the present invention shown in Figure 2, wherein, identical member is provided with identical reference character.
Mode of execution among Fig. 2 and the difference of the mode of execution among Fig. 1 are structure and the control of delivered volume flow regulator 10, and described delivered volume flow regulator consists of in the mechanical-hydraulic mode with reference to the accompanying drawings.
The regulating piston 13 of regulating piston device 11 can be loaded towards the direction that improves the delivered volume flow constantly by means of the predetermined device that is configured to spring F.
Additional or alternatively, the regulating piston 13 of regulating piston device 11 is regulated pressure by one sustainably and loaded described adjusting stress structure one predetermined device towards the direction that improves the delivered volume flow for spring F.For this reason, regulate pressure piping 16 be connected to regulating piston device 11 on the pilot pressure chamber 14 of the directive effect that improves the delivered volume flow, described spring F also is arranged in this adjusting pressure chamber, described adjusting pressure piping can in the situation that needn't in the middle of connect one and regulate pressure valve and the feeding pump of pilot pressure source 17, for example drive system and be connected the delivery line 6 of described pump 2 with the pilot pressure pump and be connected.If as shown in embodiment in regulate pressure piping 16 and described pump 2 delivery line 6 be connected pilot pressure source 17 and be connected, a selector valve device 18 that for example is configured to selector valve then can be set, and described selector valve device is connected with pilot pressure source 17 and is connected with branch line that delivery line 6 from pump 2 branches out and be connected at outlet side at input side to be regulated on the pressure piping 16.The adjusting pressure preconditioning that pump 2 among Fig. 2 passes through to occur in spring F or the adjusting pressure chamber 14 is on very big quantity delivered.
In the situation of the delivered volume flow regulator 10 of Fig. 2, the reset signal pipeline 32 that is used for the hydraulic reposition signal that guiding produces at circulating pressure balance 31 is connected to the pilot pressure chamber 15 towards the directive effect that reduces the delivered volume flow of regulating piston device 11.
Be similar to the mode of execution ground of Fig. 1, in Fig. 2, reset signal pipeline 32 can be by means of being arranged in Venturi tube 60 in the branch line 61 of container 5 towards these container 5 off-loads.
In addition, in Fig. 2, with Fig. 1 correspondingly, the cutoff device 70 of the hydraulic reposition signal that a quantity delivered that is used for causing pump 2 reduces is set, thus described hydraulic reposition signal setting in leading to the reset signal pipeline 32 of described adjusting pressure chamber 15 and in scram position 71b by the hydraulic reposition signal realize regulating piston device 11 adjusting pressure chamber 15 off-load and realize the shutoff that quantity delivered that the hydraulic reposition signal causes reduces of passing through of pump 2.
According to Fig. 1, give 32 configurations of reset signal pipeline a pressure limit device 50, utilize described pressure limit device to limit and can be adjusted in case of necessity the height of the hydraulic reposition signal of guiding in the reset signal pipeline 32.Described pressure limit device 50 in Fig. 2, be arranged in cutoff device 70 upstreams and be arranged in thus cutoff device 70 and circulating pressure balance 31 between.
Another embodiment of the present invention shown in Figure 3, wherein, identical member is provided with identical reference character.
Mode of execution among Fig. 3 and the difference of the mode of execution among Fig. 1 and 2 are structure and the control of delivered volume flow regulator 10, and described delivered volume flow regulator is configured with by the adjusting pressure valve 20 of pre-control according to Fig. 3.
In Fig. 3, the adjusting pressure chamber 14 of regulating piston device 11 is connected to and regulates on the pressure piping 16, described adjusting pressure piping by means of by two stop valves for example the selector valve device 18 that consists of of safety check be connected with delivery line 6 and/or the pilot pressure source 17 of pump 2.Additional or alternatively by the loading of regulating pressure piping 16 for regulating pressure chamber 14, in regulating pressure chamber 14, can arrange a spring assembly, described spring assembly loads the direction of delivered volume flow regulator 10 towards very big delivered volume flow.
The adjusting pressure valve 20 of loading of adjusting pressure chamber 15 of controlling described regulating piston device 11 is connected at input side in Fig. 3 and regulates on the pressure piping 16.
Regulating pressure valve 20 has towards the first control position 20a of the directive effect that reduces the delivered volume flow with towards the second control position 20b of the directive effect that improves the delivered volume flow.For this reason, regulate pressure valve 20 and be connected to one on the off-load pipeline 21 of container 5.In the first control position 20a, regulate pressure chamber 15 and be connected with adjusting pressure piping 16.Thus, in described the first control position 20a, when in regulating pressure chamber 14,15, identical adjusting pressure occurring, regulating piston device 11 because be configured to the adjusting pressure chamber 14 of the regulating piston device 11 of ladder piston, 15 difference in areas is loaded towards the direction that reduces the delivered volume flow to the right in Fig. 1.In the second control position 20b, regulate pressure chamber 15 and be connected with container 5.Thus, by the adjusting pressure that occurs in the pilot pressure chamber 14, regulating piston device 11 is loaded towards the direction that increases the delivered volume flow left in Fig. 1 in described the second control position 20b.Adjusting pressure valve 20 is configured at vertical guiding valve of neutral position throttling and rest position 20c can be set between control position 20a, 20b.
The control sliding component of regulating pressure valve 20 loads by means of the direction of a spring assembly 22 towards the first control position 20a.For the control sliding component towards the described adjusting pressure valve 20 of the direction to control of the second control position 20b, a chain of command 23 is set, described chain of command is connected with a pre-control pipeline 25.Described adjusting pressure valve 20 is configured to adjust valve in an illustrated embodiment, wherein, described control sliding component is arranged in the sleeve of a slip, and described sleeve is connected with regulating piston device 11 or the 10 formation effects of delivered volume flow regulator by mechanical coupler 26.
The pump 2 of Fig. 3 can load towards the direction that improves quantity delivered by means of the given signal of a hydraulic pressure pwc.The signal pipeline 27 of the described predetermined signal of a guiding can be connected on the described pre-control pipeline 25 for this reason.In an illustrated embodiment, signal pipeline 27 the centre connect one can be automatically controlled the situation of predetermined valve 28 under be connected to and regulate on the pressure piping 16.Described predetermined valve 28 can consist of by means of the pressure regulator valve of ratio magnet 29 motorized adjustment by one in an illustrated embodiment, utilizes described pressure regulator valve to produce corresponding predetermined pressure as the given signal of hydraulic pressure pwc in signal pipeline 27 by the pressure that occurs in the pilot line 16.By the height of described predetermined signal, can provide in advance by correspondingly controlling described adjusting pressure valve 20 the specific delivered volume flow of described pump 2, thereby so that described pump 2 carries predetermined volume flowrate to limit as volume flowrate.Preferred described predetermined signal consists of like this so that pump 2 when in pre-control pipeline 25, predetermined signal occurring (at this moment described adjusting pressure valve 20 is by the direction loading towards the second control position 20b) by preconditioning to described very big delivered volume flow.
In Fig. 3, described adjusting pressure valve 20 is configured to by the adjusting pressure valve 20 of pre-control, wherein, arrange one by the pre-control valve 40 of the hydraulic reposition SC sigmal control in the reset signal pipeline 32, thus utilize described pre-control valve can according to described hydraulic reposition signal excessively the chain of command 23 of the described adjusting pressure valve 20 of control loading and excessively control described adjusting pressure valve 20 by for reducing the loading towards the direction of the second control position 20b of the predetermined signal of the quantity delivered of pump 2.
Described pre-control valve 40 be connected to the described predetermined signal of described guiding for this reason and lead to the signal pipeline 27 of chain of command 23 of described adjusting pressure valve 20 and one lead on the off-load pipeline 41 of container 5.Described pre-control valve 40 has the first control position 40a, and in described the first control position, signal pipeline 27 is connected with described pre-control pipeline 25.In addition, in described the first control position 40a, off-load pipeline 41 is cut off.In addition, described pre-control valve 40 has the second control position 40b, and in described the second control position, pre-control pipeline 25 is connected with off-load pipeline 41.In described the second control position 40b, signal pipeline 27 is cut off.In an illustrated embodiment, described pre-control valve 40 is configured to the control valve of throttling in the neutral position, for example vertical guiding valve.
Described pre-control valve 40 loads and is loaded by the direction of the hydraulic reposition signal that guides in reset signal pipeline 32 towards the second control position 40b by means of the direction of a spring assembly 42 towards the first control position 40a.
Among Fig. 3 according to the pump 2 with electronics-hydraulic way pre-control quantity delivered of the present invention in the situation that correspondingly on the given signal of hydraulic pressure pwc of the predetermined valve 28 of electric control by being produced in signal pipeline 27 by predetermined valve 28 (it will be regulated pressure valve 20 and load towards the direction of the second control position 20b when predetermined valve is among the first control position 40a) preconditioning to one definite quantity delivered, preferred preconditioning is on very big quantity delivered, for example preconditioning is to the very big pendulum angle of the pitch of the pump that is configured to the axial flow piston machine with the pitch mode of structure.If do not have the customer V of driven system 1 to receive at this feed flow that is provided by pump 2, then circulating pressure balance 31 by the power of the discharge pressure antagonistic spring 33 of pump 2 and by in the situation that the induced pressure that one or more controlled customer V occurs in induced pressure notice pipeline 34 load towards the direction that reset signal produces position 32b, produce in the position in described reset signal, in reset signal pipeline 32, produce a hydraulic reposition signal.Loaded by the hydraulic reposition signal of the described generation direction towards the second control position 40b by the predetermined valve 40 of described hydraulic reposition SC sigmal control, wherein, thereby make and to regulate the pre-control signal off-load that pressure valve 20 loads towards the direction of the second control position and reduce on chain of command 23 to the additional signal passage of off-load pipeline 41 by pre-control pipeline 25, thereby loaded by the direction of described spring assembly 22 towards the first control position 20a so that regulate pressure valve 20, in described the first control position, delivered volume flow regulator 10 is loaded towards the direction that reduces quantity delivered, for example so that pitch back swing.Thus, utilize according to the pre-control valve 40 of described hydraulic reposition SC sigmal control and can will excessively control to reduce quantity delivered to the pump 2 that presets quantity delivered by described hydraulic reposition signal by the predetermined Signal Regulation in the described signal pipeline 27.Can be required according to the conveying stream of customer V to be retrieved and to reduce thus to the delivered volume stream that the pump 2 of predetermined quantity delivered provides by preconditioning.That realizes thus is the excess volume stream that minimizing and restriction surpass customer V demand and carried by pump 2.
In Fig. 3, be similar to the embodiment ground of Fig. 1 and 2, reset signal pipeline 32 can be by means of being arranged in Venturi tube 60 in the branch line 61 of container 5 towards container 5 off-loads.
In addition, in Fig. 3, with Fig. 1 and 2 correspondingly, arrange one for the cutoff device 70 of the hydraulic reposition signal of the quantity delivered reduction that causes pump 2, described hydraulic reposition signal is arranged in the reset signal pipeline 32 of pre-control valve 40, in described scram position 71b, allow to be realized by described hydraulic reposition signal the off-load of the control gear of pre-control valve 40, wherein, by described pre-control valve 40 is loaded into the shutoff that back swings that described hydraulic reposition signal causes of passing through that realizes pump 2 among the first control position 40a by spring assembly 42.
According to Fig. 1 and 2, give 32 configurations of reset signal pipeline one pressure limit control valve unit 50, utilize described pressure limit control valve unit to limit and can be adjusted in case of necessity the height of the hydraulic reposition signal of guiding in the described reset signal pipeline 32.
In Fig. 3, the electric control device of controlling described predetermined valve 28 and cutoff device 70 or control valve 7 is not shown specifically.
The present invention has series of advantages.
To the pressure limit device 50 of described reset signal pipeline 32 and the configuration Venturi tube 60 to described reset signal pipeline 32, can in the situation of the different control programs of the proportioner 10 with different adjustment stress level and make, use flexibly and simply quantity delivered control gear of the present invention by configuration.The pressure altitude of the adjusting pressure in the hydraulic reposition signal in the reset signal pipeline 32 and the adjusting pressure piping 16 can reach very big pumping pressure at this always.
Thereby utilize shut-off valve 71 can be in specific running state the improvement of power performance of implement of interruption function drive system 1 by the hydraulic reposition signal of controlling and passing through to produce (it causes the reduction of the quantity delivered of pump 2) in scram position 71b.The quantity delivered reduction that prevents pump 2 in the situation by the stop valve 71 in being in scram position 71b can be in the situation that specific customer motion realizes the power performance of the remarkable improvement of drive system 1.Quick and the multiple speed that this customer motion for example is customer changes, and utilizes described speed to change the chatter that should realize on the customer V.In the situation of the excavator that is configured to have drive system of the present invention, this chatter can expect at the customer V of control one bucket, so that the stoichiometric equation of permission bucket is emptying.
Thus, obtain the advantage of the little energy consumption aspect of the simple co-ordination possibility of described drive system 1 and drive system 1 in conjunction with pressure limit device 50, Venturi tube 60 and/or cutoff device 70.
Claims (8)
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102011107222.9 | 2011-07-13 | ||
| DE102011107222A DE102011107222A1 (en) | 2011-07-13 | 2011-07-13 | Hydrostatic drive system with a pump adjustable in the delivery volume |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN102878127A true CN102878127A (en) | 2013-01-16 |
| CN102878127B CN102878127B (en) | 2016-05-04 |
Family
ID=47425575
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201210243843.5A Expired - Fee Related CN102878127B (en) | 2011-07-13 | 2012-07-13 | Hydrostatic drive system |
Country Status (3)
| Country | Link |
|---|---|
| JP (1) | JP6218363B2 (en) |
| CN (1) | CN102878127B (en) |
| DE (1) | DE102011107222A1 (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105041748A (en) * | 2014-04-29 | 2015-11-11 | 罗伯特·博世有限公司 | Hydraulic control arrangement for a plurality of actuators |
| CN112661072A (en) * | 2020-12-14 | 2021-04-16 | 中国煤炭科工集团太原研究院有限公司 | Shake eliminating system, method and device for lifting workbench |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102014109203B4 (en) | 2013-12-18 | 2023-09-21 | Linde Hydraulics Gmbh & Co. Kg | Hydrostatic pump of a demand flow-controlled hydrostatic drive system |
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| DE102008038382A1 (en) * | 2008-08-19 | 2010-02-25 | Linde Material Handling Gmbh | Hydrostatic drive system, particularly load-sensing drive system, has pump adjusted in delivery volume, where pump is provided for supplying load and is formed as hydraulically adjustable pump in delivery volume |
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| JPS5670106A (en) * | 1979-11-12 | 1981-06-11 | Daikin Ind Ltd | Combination fluid circuit |
| JPS5937305A (en) * | 1983-04-07 | 1984-02-29 | Daikin Ind Ltd | Hydraulic equipment |
| US4813235A (en) * | 1987-06-09 | 1989-03-21 | Deere & Company | Hydraulic gain reduction circuit |
| JPH01128001U (en) * | 1988-02-24 | 1989-08-31 | ||
| JP2677880B2 (en) * | 1989-09-30 | 1997-11-17 | 株式会社トキメック | Load sensing circuit |
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- 2011-07-13 DE DE102011107222A patent/DE102011107222A1/en not_active Withdrawn
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- 2012-07-13 CN CN201210243843.5A patent/CN102878127B/en not_active Expired - Fee Related
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE3535771A1 (en) * | 1985-10-07 | 1987-04-09 | Linde Ag | HYDROSTATIC DRIVE WITH SEVERAL CONSUMERS |
| US5562019A (en) * | 1992-10-22 | 1996-10-08 | Linde Aktiengesellschaft | Hydrostatic drive system |
| DE19538649A1 (en) * | 1995-10-17 | 1997-04-24 | Brueninghaus Hydromatik Gmbh | Power control with load sensing |
| CN101371049A (en) * | 2006-04-27 | 2009-02-18 | 日立建机株式会社 | inertial body drive |
| DE102008038381A1 (en) * | 2007-12-19 | 2009-06-25 | Linde Material Handling Gmbh | Hydrostatic drive system for use in e.g. excavator, has pump designed as electric-hydraulic displaceable pump so that displacement volume control device is movable in direction of reduction of displacement volume by hydraulic backup signals |
| DE102008038382A1 (en) * | 2008-08-19 | 2010-02-25 | Linde Material Handling Gmbh | Hydrostatic drive system, particularly load-sensing drive system, has pump adjusted in delivery volume, where pump is provided for supplying load and is formed as hydraulically adjustable pump in delivery volume |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105041748A (en) * | 2014-04-29 | 2015-11-11 | 罗伯特·博世有限公司 | Hydraulic control arrangement for a plurality of actuators |
| CN105041748B (en) * | 2014-04-29 | 2019-03-22 | 罗伯特·博世有限公司 | Hydraulic control device for multiple actuators |
| CN112661072A (en) * | 2020-12-14 | 2021-04-16 | 中国煤炭科工集团太原研究院有限公司 | Shake eliminating system, method and device for lifting workbench |
| CN112661072B (en) * | 2020-12-14 | 2022-08-12 | 中国煤炭科工集团太原研究院有限公司 | Shake eliminating system, method and device for lifting workbench |
Also Published As
| Publication number | Publication date |
|---|---|
| CN102878127B (en) | 2016-05-04 |
| JP6218363B2 (en) | 2017-10-25 |
| DE102011107222A1 (en) | 2013-01-17 |
| JP2013019414A (en) | 2013-01-31 |
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