CN103261706A - Hydraulic driver - Google Patents
Hydraulic driver Download PDFInfo
- Publication number
- CN103261706A CN103261706A CN201180062030XA CN201180062030A CN103261706A CN 103261706 A CN103261706 A CN 103261706A CN 201180062030X A CN201180062030X A CN 201180062030XA CN 201180062030 A CN201180062030 A CN 201180062030A CN 103261706 A CN103261706 A CN 103261706A
- Authority
- CN
- China
- Prior art keywords
- pump
- pressure
- torque
- fluid pressure
- drive device
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
- F04B49/06—Control using electricity
- F04B49/065—Control using electricity and making use of computers
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B17/00—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
- F04B17/03—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors
-
- 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
- F15B11/042—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the feed line, i.e. "meter in"
- F15B11/0423—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the feed line, i.e. "meter in" by controlling pump output or bypass, other than to maintain constant speed
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B2203/00—Motor parameters
- F04B2203/02—Motor parameters of rotating electric motors
- F04B2203/0207—Torque
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B2205/00—Fluid parameters
- F04B2205/06—Pressure in a (hydraulic) circuit
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
- F15B2211/205—Systems with pumps
- F15B2211/20507—Type of prime mover
- F15B2211/20515—Electric motor
-
- 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
-
- 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
- F15B2211/26—Power control functions
-
- 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
- F15B2211/6306—Electronic controllers using input signals representing a pressure
- F15B2211/6309—Electronic controllers using input signals representing a pressure the pressure being a pressure source supply pressure
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/60—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
-
- 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
- F15B2211/6333—Electronic controllers using input signals representing a state of the pressure source, e.g. swash plate angle
-
- 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
- F15B2211/6651—Control of the prime mover, e.g. control of the output torque or rotational speed
-
- 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
- F15B2211/6652—Control of the pressure source, e.g. control of the swash plate angle
-
- 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
- F15B2211/6655—Power control, e.g. combined pressure and flow rate control
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Computer Hardware Design (AREA)
- Control Of Positive-Displacement Pumps (AREA)
- Reciprocating Pumps (AREA)
Abstract
The invention relates to a hydraulic driver for a hydraulic load or for a hydraulic system. The hydraulic driver has a variable-displacement pump which is mechanically coupled to a preferably variable-speed drive motor, and a control for adjusting at least the capacity of the pump and optionally the speed of the drive motor. According to the invention a torque detecting or determining device is provided which detects or calculates a current output torque of the drive motor, wherein in response thereto the capacity of the pump is set to a value at which the current output torque is at or below a set maximum value.
Description
Technical field
The present invention relates to a kind of as described in the preamble, fluid pressure drive device of being used for hydraulic load according to Patent right requirement 1.
Background technique
By prior art according to the known such fluid pressure drive device of document EP 1 387 090 A2.This fluid pressure drive device has been stipulated the structure of the electric motor that rotating speed is variable, and the variable electric motor of described rotating speed drives two metering pumps in this case.At least one pump in the described pump can on/off according to present load pressure, and its mode switches to cycle operation (Umlauf) alternatively for the pump that will preferably have bigger stroke capacity.By this way can be with relatively little torque design motor drive.
Document EP 0 805 922 B1 disclose a kind of hydraulic pump control of aircraft, and described hydraulic pump control uses the variable oil hydraulic pump of the amount of squeezing, and the variable oil hydraulic pump of the described amount of squeezing is by the variable electrical motor driven of rotating speed.At the rotating speed of this governor motor, make its reduction rate when system requirements reduces less than its Magnification when system requirements raises.This means, for example when demand pressure reduces, at first reduce the throw of pump capacity, otherwise when demand pressure raises, at first increase motor rotary speed.
As other prior aries by the same known a kind of hydro-electric driver element of document EP 464 286 B1.Described driver element uses the electric motor that can rotating speed moves changeably to be used for driving and adjusts pump.By spring described adjustment pump is adjusted on the position with maximum stroke capacity at this, when the rising of the pressure in the hydraulic system surpasses the force value of determining, described adjustment pump is adjusted from described position towards the minimal stroke capacity.
At last, document DE 10 2,007 007 005 A1 disclose a kind of electrohydraulic control equipment with the variable pump of the amount of squeezing, and described electric hydaulic control apparatus is by the variable electrical motor driven of rotating speed.Be provided with two-point regulator (Zweipunktregler) in order to control described pump, described two-point regulator switches to described pump on the maximum or minimum transfer position, according to the state that exceeds the state of pressure threshold or be lower than pressure threshold described pump is switched on the maximum or minimum transfer position or rather.
Summary of the invention
Based on above-mentioned prior art, task of the present invention is to provide a kind of fluid pressure drive device for hydraulic system, described fluid pressure drive device is made up of the amount of squeezing variable (stroke capacity is variable) pressure medium source (oil hydraulic pump) and the variable drive motor of rotating speed at least, and wherein said drive unit has with respect to the improved characteristic of prior art.Its target is, makes fluid pressure drive device inexpensively.Another target is, reduces the cost of regulation technology.Last target of the present invention is, especially drive motor reduced according to the design principle of " lightweight compact type (downsizing) ", and can not endanger the functional safety of rearmounted hydraulic system.
The fluid pressure drive device of the feature of proposing of task by having Patent right requirement 1 solves.Favourable design proposal of the present invention is the theme of dependent claims.
Therefore, the present invention relates to a kind of for one/a plurality of loads or be used for the fluid pressure drive device of hydraulic system, described fluid pressure drive device has the variable pump of the amount of squeezing and controller, the variable drive motor of described pump and rotating speed mechanically couples, and described controller is used for adjusting the throw of pump capacity.According to the present invention described pump is carried out torque adjustment.In other words, should not surpass the torque of determining in order to drive described pump.Even as long as also be lower than definite torque by the product torque that draw, that be described to the desired pressure medium amount of described pump revolution of system pressure and stroke capacity when the maximum stroke capacity, torque adjustment just stays out of so.If it is that determined by load or can predefined pressure so high by pressure valve when in accelerating process and at the backstop place, load being arranged, thereby make the product of pressure and stroke capacity reach predefined value, so described pump is adjusted towards the small stroke capacity.It is constant at least approx that the product of described pressure and stroke capacity keeps.
Can use the drive motor with relatively little peak torque in this case, thus described drive unit become more with low cost on the whole and its operation because the power consumpiton that reduces of motor also becomes more economical.
At this, should be set at the device that each is suitable for deriving the current torque load(ing) of drive motor for concept " torque verifying attachment/or torque determine device ".Described device for example can be to be positioned at the torque sensor on drive motor or its driven shaft or to measure the current current drain of described motor and determine the current measurement device of the torque of output thus.Also have following scheme, detection places current pressure and control ground or the adjusting ground adjustment stroke capacity of the hydraulic system of described pump back, thereby makes described stroke capacity be no more than predefined peak torque.
Particularly advantageously be, will be for adjusting pump known torque controller as " torque verifying attachment/or torque determine device ", wherein the valve piston of modulating valve is adjusted that direction is loaded by the spring force that pre-determines maximum moment and is adjusted direction by being loaded by the power pumping pressure loaded piston, that draw according to the point of action (Angriffpunkt) of stroke capacity along another on rocking bar along one.
Described drive motor is that rotating speed is variable.If reduce described throw of pump capacity accordingly, to limit needed torque on the motor, the motion that then causes the hydraulic pressure of one or more load (for example lifting jar) to cause is slack-off.If keep described motion, can when reducing, improve the throw of pump capacity rotating speed of drive motor, and the volume flowrate that is produced by the pump of putting back increases again according to rotating speed thus, and does not increase the output torque.
If yet the load of hydraulic pressure is positioned at the backstop place when pressure raises, only keeps a pressure, thereby do not improve, reduce or rather on the contrary the rotating speed of drive motor.
, the power consumpiton of motor can be remained on basically and (be similar to) under the constant value according to the torque adjustment pressure medium source by directly/indirectly, thereby make described motor to design at the power output facet of its maximum possible lessly.
Description of drawings
Next the present invention is explained in detail with reference to accompanying drawing by preferred embodiment.
Fig. 1 shows at this with contrasting:
-according to fluid pressure drive device prior art, that have the pump of two less stroke capacity that drive separately;
-according to prior art, have a fluid pressure drive device lasting and metering pump that can connect; And
-according to the fluid pressure drive device of the variable drive motor of the variable pump of the amount of squeezing preferred embodiment of the present invention, that have torque control and rotating speed; And
Fig. 2 shows fluid pressure governor/controller and is used for
-pressure medium source, especially
The variable pump of-amount of squeezing according to the present invention.
Embodiment
A kind of known fluid pressure drive device has been shown in the diagram according to appended Fig. 1 on the left side, and described fluid pressure drive device uses the metering pump of two drive.Therefore each pump is by own, the variable motor driving of rotating speed in case of necessity.This structure is relative complex and costliness.Have bigger space requirement in addition, this technological scheme is uneconomic more precisely thus.
The same known fluid pressure drive device of diagram in the middle of with reference to the accompanying drawings provides a kind of improvement project.This drive unit is same to use two metering pumps, but described metering pump is driven jointly by unique motor.Described metering pump one of them can be by valve, be directly switch to alternatively on the storage tank at this bi-bit bi-pass switching valve that for example has open position and locked position of coupler, described pump is adopted by the hydraulic system of postposition thus.Can unload motor by this way.
Relative therewith, the diagram on middle the right shows according to fluid pressure drive device 1 of the present invention with reference to the accompanying drawings.
Therefore, unique pump 2 only is set, it is variable that described pump is configured to the amount of squeezing.For example described pump 2 can be configured to swash plate pump, and its swash plate gradient can change continuously or step by step.Pump 2 is connected on the hydraulic system 4 at outlet side, for example is made up of control valve 6, can handle load 8, be piston-cylinder unit at this by described control valve.
Described unique variable pump 2 of the amount of squeezing is moved by drive motor 10, for example electric motor unique, that preferred rotating speed is variable, and described drive motor mechanically couples by live axle and pump 2.
At last, be provided for the control unit 11 of drive motor 10, be connected on the described control unit at this at least one torque sensor and system pressure sensor and speed probe with for detection of the sensor (not shown all the sensors) of the stroke capacity (swash plate gradient) of the current adjustment of pump 2.At this control unit 11 is programmed or can be programmed, thereby make that described fluid pressure drive device 1 makes up and maintenance can predetermined (can provide) induced pressure or system pressure.
According to the present invention, use the drive motor 10 with relatively little power, described drive motor only can be realized little maximum output torque.Therefore when reaching this maximum output torque or being lower than this maximum output torque, the variable pump 2 of rollback (the zur ü ckfahren) amount of squeezing under the situation about raising of the pressure in hydraulic system for example, just reduce its transmission capacity, reduce the current output torque of drive motor 10 thus.Can adjust described pump 2 or its stroke capacity by this way, thereby irrespectively make the current output torque of motor 10 be no more than maximum torque value or keep below described maximum torque value with pressure state in the hydraulic system of postposition.Under favourable situation, described output torque can keep constant basically.That is to say, be suitable for equation P * V=constant=T, wherein
P: the actual pressure in the hydraulic system;
V: the actual stroke capacity of pump;
T: the actual output torque of motor.
If the transmission capacity of rollback pump 2 by this way, it is slack-off then to be applied to the motion that hydraulic pressure in the load reduces thus or the hydraulic pressure of load activates.For fear of this point, preferred embodiment according to the present invention stipulates that alternatively rotating speed is constructed drive motor 10 changeably.Therefore, when the transmission capacity of pump 2 reduces in order to keep exporting the constant rotating speed that can improve motor 10 of torque, to keep desired present load pressure or load movement speed for this reason.
About controlling referring to the circuti diagram according to Fig. 2 of the variable pump 2 of this pressure medium source or the amount of squeezing, described circuti diagram shows the diagram according to pressure medium pump of the present invention.Wherein in housing 12, can find out and have cylindrical drum 40, live axle 22, swash plate 43, limit and adjust showing piston 75, showing the Returnning spring 85 on the piston 75 and limiting the fluid pressure drive device that swings in piston 76 of adjusting chamber 102 of chamber 101.High-pressure channel 103 and low-pressure channel or suction passage 104 extend in housing 12.Described adjustment chamber 101 is connected with high-pressure channel 103 constantly by path 10 5.Modulating valve 80 is configured on the housing 12.This modulating valve is made of torque adjusting parts valve 106 and pressure regulating part valve 107, described pressure regulating part valve in position of rest by first entrance with and adjust mouthful a adjusting with torque adjusting parts valve 106 and export to pilot line 108 and connect, described pilot line leads to the adjustment chamber 102 that swings in piston 76 places.Second entrance of pressure regulating part valve 107 is connected with high-pressure channel 103.The entrance of same torque adjusting parts valve 106 is connected with high-pressure channel 103, and second entrance of torque adjusting parts valve 106 opens wide with respect to inside housing 12, that have storage tank pressure.The regulating piston of pressure regulating part valve 107 on the meaning of the angle of oscillation that dwindles swash plate 43 by the pressure-loaded in the pressure duct 103 and be in reverse to adjustable spring and load.
In the housing 95 of valve 80, be supported with the rocking bar 115 of both arms, on described rocking bar, in the housing of rollback element (R ü ckf ü hrelement), guide and by path 10 5, adjust chamber 101 and the hole 92 of showing in the piston 75 is applied on one of them rocker arm with the piston 116 of the pressure-loaded in the high-pressure channel 103.Removing of point of action utilizes the angle of oscillation of swash plate 43 to change.Another arm of described rocking bar 115 is the end of the regulating piston of torque adjusting parts valve 106 and approximate acting on opposed to each other between the spring 117 on the described rocker arm, that can adjust at least.In addition, the regulating piston to described torque adjusting parts valve 106 is loaded by adjustable spring 118 towards rocker arm.Described spring 117 and the torque of fixing in rocking bar 115 formation along a direction more weakly than the spring 118 that spring 117 is adjusted.High pressure in path 10 3 forms torque by the acting surface of piston 116 at rocking bar 115, and described torque is pointed on the contrary with fixing torque and depended on the position of showing piston 75 or the angle of oscillation that depends on swash plate 43 usually.Under the situation of pressure given, only can when determining, angle of oscillation make the torque that is formed by two springs keep balance.Under the situation of described balance disorder, make the valve piston of torque adjusting parts valve 106 move from its adjusted position by changing pressure, thereby make pressure medium can flow to described adjustment chamber 102 or pressure medium can flow out from described adjustment chamber 102, up to reaching another angle of oscillation, formed balance between the torque on the rocking bar 115 again at this.
Therefore, if improve hydraulic system pressure and then improve pressure in the pipeline 103, spur the valve piston of torque adjustment valve 106 so to the right according to Fig. 2, described system pressure is applied to by pipeline 108 and swings on the piston 76 thus.This gradient that reduces swash plate 43 thus torque balance occurs on rocker arm 115.Therefore the driving torque by described motor output that is applied on the axle 22 can keep constant.
Claims (4)
1. fluid pressure drive device that is used for hydraulic load (8) or is used for hydraulic system (4), described fluid pressure drive device has the variable pump of the amount of squeezing (2) and controller (12), the variable drive motor (10) of described pump and rotating speed mechanically couples, described controller is used for adjusting the stroke capacity of described pump (2), it is characterized in that, described pump (2) is carried out torque adjustment.
2. by the described fluid pressure drive device of claim 1, it is characterized in that for detection of described load (8) locate or described hydraulic system (4) in pressure-detecting device or the pressure of current pressure determine device, wherein so adjust described pump (2), namely be suitable for equation T=constant=P * V, T(constant wherein)=the predetermined output torque value of described drive motor, P=induced pressure/hydraulic system pressure, and the described throw of pump capacity of V=.
3. by the described fluid pressure drive device of claim 2, it is characterized in that described pump (2) is equipped with mechanical-hydraulic torque controller (106).
4. by each described fluid pressure drive device in the claim 1 to 3, it is characterized in that, adjust the rotating speed of described drive motor (10) according to the current stroke capacity of described pump (2), thereby obtain the predetermined movement velocity of described hydraulic load.
Applications Claiming Priority (5)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102010055864.8 | 2010-12-22 | ||
| DE102010055864 | 2010-12-22 | ||
| DE102011108285A DE102011108285A1 (en) | 2010-12-22 | 2011-07-21 | Hydraulic drive |
| DE102011108285.2 | 2011-07-21 | ||
| PCT/EP2011/005668 WO2012084093A1 (en) | 2010-12-22 | 2011-11-11 | Hydraulic drive |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN103261706A true CN103261706A (en) | 2013-08-21 |
| CN103261706B CN103261706B (en) | 2016-11-30 |
Family
ID=
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109838421A (en) * | 2017-11-28 | 2019-06-04 | B和R工业自动化有限公司 | Hydraulic system with servo drive and hydraulic consumers device and the control device for the hydraulic system |
Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE1922145A1 (en) * | 1969-04-25 | 1970-10-29 | Bellows Valvair Kaemper Gmbh | Combination controller |
| DE1911695A1 (en) * | 1969-03-03 | 1970-11-19 | Mannesmann Meer Ag | Power regulator for hydraulic pumps or motors |
| EP0402871A2 (en) * | 1989-06-12 | 1990-12-19 | Brueninghaus Hydromatik Gmbh | Control device for variable displacement pump |
| US5052909A (en) * | 1990-01-19 | 1991-10-01 | Cincinnati Milacron Inc. | Energy-conserving injection molding machine |
| US5865602A (en) * | 1995-03-14 | 1999-02-02 | The Boeing Company | Aircraft hydraulic pump control system |
| EP1387090A2 (en) * | 2002-08-02 | 2004-02-04 | Bosch Rexroth AG | Hydraulic drive |
| CN101594977A (en) * | 2007-02-08 | 2009-12-02 | 罗伯特·博世有限公司 | Electro-hydraulic control apparatus |
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE1911695A1 (en) * | 1969-03-03 | 1970-11-19 | Mannesmann Meer Ag | Power regulator for hydraulic pumps or motors |
| DE1922145A1 (en) * | 1969-04-25 | 1970-10-29 | Bellows Valvair Kaemper Gmbh | Combination controller |
| EP0402871A2 (en) * | 1989-06-12 | 1990-12-19 | Brueninghaus Hydromatik Gmbh | Control device for variable displacement pump |
| US5052909A (en) * | 1990-01-19 | 1991-10-01 | Cincinnati Milacron Inc. | Energy-conserving injection molding machine |
| US5865602A (en) * | 1995-03-14 | 1999-02-02 | The Boeing Company | Aircraft hydraulic pump control system |
| EP1387090A2 (en) * | 2002-08-02 | 2004-02-04 | Bosch Rexroth AG | Hydraulic drive |
| CN101594977A (en) * | 2007-02-08 | 2009-12-02 | 罗伯特·博世有限公司 | Electro-hydraulic control apparatus |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109838421A (en) * | 2017-11-28 | 2019-06-04 | B和R工业自动化有限公司 | Hydraulic system with servo drive and hydraulic consumers device and the control device for the hydraulic system |
Also Published As
| Publication number | Publication date |
|---|---|
| TW201239206A (en) | 2012-10-01 |
| DE102011108285A1 (en) | 2012-06-28 |
| US20130336812A1 (en) | 2013-12-19 |
| EP2655895A1 (en) | 2013-10-30 |
| EP2655895B1 (en) | 2020-01-22 |
| TWI608172B (en) | 2017-12-11 |
| WO2012084093A1 (en) | 2012-06-28 |
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