CN105378298A - Hydraulic system - Google Patents
Hydraulic system Download PDFInfo
- Publication number
- CN105378298A CN105378298A CN201480038144.4A CN201480038144A CN105378298A CN 105378298 A CN105378298 A CN 105378298A CN 201480038144 A CN201480038144 A CN 201480038144A CN 105378298 A CN105378298 A CN 105378298A
- Authority
- CN
- China
- Prior art keywords
- pressure
- valve
- clutch
- hydraulic system
- limit
- 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
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Classifications
-
- 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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D48/00—External control of clutches
- F16D48/02—Control by fluid pressure
- F16D48/0206—Control by fluid pressure in a system with a plurality of fluid-actuated clutches
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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
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
- F15B13/023—Excess flow valves, e.g. for locking cylinders in case of hose burst
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
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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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D48/00—External control of clutches
- F16D48/02—Control by fluid pressure
- F16D2048/0209—Control by fluid pressure characterised by fluid valves having control pistons, e.g. spools
-
- 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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D48/00—External control of clutches
- F16D48/02—Control by fluid pressure
- F16D2048/0221—Valves for clutch control systems; Details thereof
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
The invention relates to a hydraulic system having a pressure-limiting valve which has a limit pressure that can be increased by actuation. The invention is characterized in that the pressure-limiting valve is combined with a device for providing an additional pressure reduction function.
Description
Technical field
The present invention relates to a kind of hydraulic system with pressure-limit valve, described pressure-limit valve has ultimate pressure, and described ultimate pressure can improve by operating.The invention still further relates to a kind of method for running this hydraulic system.
Background technique
From International publication WO2007/054051A2, become known for equipment and the method for determining motor deboost, wherein the clutch actuator of automatic shifting transmission keeps not moving.The hydraulic pressure installation with motor and oil hydraulic pump of operated clutch is become known for from German laid-open document DE102012202162A1, wherein valve can be provided with in order to be remained in target location by clutch, once clutch reaches target location, described valve is with regard to the underground between canned pump and clutch.Known a kind of hydrostatic clutch with gear pump from Germany Patent document DE3004581C2, described clutch is at least equipped with pressure-limit valve in order to avoid torque peak.
Summary of the invention
The object of the invention is: improve ride quality and/or the response performance with the hydraulic system of pressure-limit valve, described pressure-limit valve has ultimate pressure, and described ultimate pressure can improve by operating.
This object realizes in the following way in the hydraulic system with pressure-limit valve: combined with being used for providing the device of additional pressure-reducing function by pressure-limit valve, wherein said pressure-limit valve has ultimate pressure, and described ultimate pressure can improve by operating.When meeting or exceeding ultimate pressure, usually open pressure-limit valve.The additional pressure-reducing function of pressure-limit valve realizes opening pressure-limit valve when pressure is less than ultimate pressure.Thus in a straightforward manner with method in order to diagnostic purpose realizes opening of pressure-limit valve.In addition, the system pressure in hydraulic system can be reduced rapidly by additional pressure-reducing function, even if also like this when system pressure is less than ultimate pressure.
The feature of a preferred embodiment of hydraulic system is: have pressure-reduction outlet for providing the device of additional pressure-reducing function.Can via pressure-reduction outlet pressure be reduced in low pressure range or be reduced to the pressure in liquid-storage container.
The feature of another preferred embodiment of hydraulic system is: pressure-reduction outlet is arranged between the two seals.Therefore pressure-reduction outlet forms or forms similarly with it as the vent in the clutch master cylinder of routine.
The feature of another preferred embodiment of hydraulic system is: pressure-reduction outlet can be closed by valve piston.Valve piston defines annular chamber in inner radial, and described annular chamber is in axial direction by two Sealing gauges.At radially outer, annular chamber is by valve chest gauge, and described valve chest has pressure-reduction outlet.
The feature of another preferred embodiment of hydraulic system is: valve piston is tightened in operating position in advance by closing spring, and in described operating position, pressure-reduction outlet is closed.Operating position limits advantageous by blocked part, valve piston in operating position backstop on described blocked part.
The feature of another preferred embodiment of hydraulic system is: final controlling element is attached troops to a unit in valve piston, and valve piston is held in its operating position by additional trying hard to keep by described final controlling element.That the additional power be applied on valve piston such as can pass through electricity or that electronics is hydrostatic final controlling element applies.
The feature of another preferred embodiment of hydraulic system is: valve piston in closed blocked part and can open to-and-fro motion between blocked part, described in open blocked part limit open position, in described open position, pressure-reduction outlet is discharged by valve piston.The limit position of the restriction of valve piston can be provided with method in a straightforward manner by these two blocked parts.
The feature of another preferred embodiment of hydraulic system is: pressure-limit valve is attached troops to a unit in cut-off clutch, and described cut-off clutch is by the operation of hydrostatic clutch actuator.Cut-off clutch is preferably hybrid cut-off clutch, and described hybrid cut-off clutch, by the operation of hydrostatic clutch actuator, is namely opened and/or closed.In hybrid cut-off clutch, distinguish sliding between startup (Schlupfstart) and pulse enable (Impulsstart).When pulse enable, the rotary pulse (Drehimpuls) of motor is used to carry out starting apparatus combustion engine.But this needs following feasibility: cut-off clutch closes extremely rapidly.In this article, pressure-limit valve according to the present invention turns out to be is favourable.Can open, to reduce system pressure more quickly by the hydrostatic clutch actuator of operation according to pressure-limit valve of the present invention simultaneously.Improve the pulse enable performance of automatically closed cut-off clutch thus significantly.
The feature of another preferred embodiment of hydraulic system is: pressure-limit valve is attached troops to a unit in the hydrostatic circuit of the clutch system of hydrostatic operation.The clutch system of hydrostatic operation is preferably the double clutch system of hydrostatic operation, and described double clutch system has two hydrostatic circuits, for two sub-clutch circuits of hydrostatic operation double clutch.Advantageously, described hydrostatic circuit is equipped with one respectively according to pressure-limit valve circuit of the present invention.The sub-clutch of double clutch system is preferably directly via hydrostatic line loop operation.In order to this object, the piston of master cylinder can be regulated electrically.Slave cylinder is via the operation of in hydrostatic circuit.The piston of slave cylinder preferably directly acts on clutch plate at this, clamps the driven disc of sub-clutch and then realize torque via closed sub-clutch transmission by means of described clutch plate.When sub-clutch is opened, preloading spring can overcome slave cylinder piston action and for keeping the minimum fluid pressure in hydrostatic operation system.Sub-clutch closes usually as required, can transmit required torque.Operate pressure-limit valve by electricity, can ultimate pressure be improved, even if make also to keep corresponding hydrostatic circuit sealing when operating pressure is maximum.Advantageously realize the self-retaining function that the double clutch system of hydrostatic operation is provided thus.When electric operation equipment is malfunctioning, such as, can be guaranteed with method in a straightforward manner by suitable spring pre-tightening: corresponding pressure-limit valve or this two pressure-limit valves are trouble-freely opened.Thereby, it is possible to realize with method in a straightforward manner: one or more pressure-limit valve is only opened in case of a fault.Thus, such as, when valve is configured to guiding valve, the less desirable dirt at the valve seat place of pressure-limit valve can be avoided.In the embodiment of valve with valve piston, dirt can not be anticipated.By one or more pressure-limit valve according to design of the present invention, especially favourablely additionally realize diagnostic function.Under the state that pressure-limit valve does not operate, preferably under the cold state of pressure-limit valve of electricity operation, valve piston, advantageous by closing spring pretension consumingly, makes valve piston to recline regularly closed blocked part.Pressure-reduction outlet is closed.When pressure increase, pressure-limit valve do not operate or under cold state, system pressure is enough to open valve piston through pressure-reduction outlet, so that the pressure in reduction system extremely rapidly.Thereby, it is possible to provide the clutch system automatically opened in a straightforward manner with method.
The present invention also relates to a kind of method for running above-mentioned hydraulic system.Achieve the clutch system providing a kind of hydrostatic operation in a straightforward manner with method according to method of the present invention, especially double clutch system, it has the automatic maintenance function that can diagnose.
Superpressure activation threshold value for ultimate pressure is promoted by such as electric operation equipment, makes not open one or more pressure-limit valve when normal operation.In normal operation, one or more pressure-limit valve is reliably sealed by such as electric operation equipment.During central power operation device, the pressure-limit valve so sealed advantageously only is opened in case of a fault.By the diagnostic function described before especially advantageously the realizing according to design of the present invention of one or more pressure-limit valve.
Accompanying drawing explanation
Other feature, advantage and details of the present invention draws from the following description, in described description, describe different embodiments in detail with reference to accompanying drawing.It illustrates:
Fig. 1 has the diagram of the extreme facility of the double clutch system of the hydrostatic operation of two hydrostatic circuits, and described circuit has the pressure-limit valve of two electric control;
Fig. 2 illustrates and similar diagram in Fig. 1, and wherein two pressure-limit valves are controlled by common electric valve actuator;
Fig. 3 illustrates the reduced graph according to pressure-limit valve of the present invention of the valve piston had in operating position, and
Fig. 4 illustrates the pressure-limit valve in the Fig. 3 of the valve piston had in open position.
Embodiment
The double clutch system 10 of the hydrostatic operation with two hydrostatic circuits 11,12 is shown in fig 1 and 2 extreme facility.Hydrostatic circuit 11,12 is for (unshowned) sub-clutch of directly operating dual clutch device.A clutch slave cylinder is connected with a clutch master cylinder by hydrostatic circuit 11,12 respectively.
In clutch master cylinder, be provided with piston, described piston regulates electrically.The adjustment movement of the piston of clutch master cylinder is delivered on the piston belonging to clutch slave cylinder via hydraulic medium, as hydraulic oil by underground 11,12.The piston of clutch slave cylinder is advantageously applied directly on the clutch plate of corresponding sub-clutch.
Every sub-clutch is equipped with the clutch plate and driven disc that connect from different transmission input shafts.When sub-clutch is opened, preloading spring is against the piston action of corresponding slave cylinder.Guaranteed by preloading spring: minimally hydraulic pressure in underground 11,12.Sub-clutch is advantageously only closed, can transmit required torque as required strategic point by motorized adjustment piston in master cylinder.
The motorized adjustment of master cylinder piston realizes via electric actuator, and described final controlling element is formed in self-sustaining mode due to relatively high velocity ratio.Due to self-sustaining, sub-clutch is not automatically opened when electric part fails.For the reason of safety, therefore, in the double clutch operation system of routine, two hydrostatic circuits are equipped with control apparatus respectively, and described control apparatus comprises two processors.Guaranteed by these two control apparatuss: even if an electric actuator also can be opened when another electric actuator is no longer made a response.The less desirable clamping in speed changer can be stoped thus.
It is relatively costly for applying two equivalent control apparatuss.In addition, in the double clutch system of routine, even if only also open the corresponding electric actuator system worked when the control apparatus that application two is equivalent.
These two hydrostatic circuits 11,12 are equipped with a pressure-limit valve 15,16 respectively; 25,26.Via pressure-limit valve 15,16; 25,26, the superpressure in underground 11,12 can be reduced in bank 17,18 or in bank 28.
Shown by the symbol 21,22 of the spring representing pretension in FIG: when exceeding the value preset by initial tension of spring, pressure-limit valve 15,16 is opened.Setting ultimate pressure by initial tension of spring 21,22, opening pressure-limit valve 15,16 when overstepping the extreme limit pressure in case of a fault.
Shown by other symbol 23,24: the ultimate pressure set by means of spring 21,22 can be improved into by electric valve actuator, even if make to close substantially beyond also keeping the hydrostatic circuit 11,12 distributing to pressure-limit valve 15,16 when the ultimate pressure set by spring 21,22 at pressure.
Can be realized in a straightforward manner by means of electric valve actuator 23,24 by suitable control strategy (such as when valve is configured to guiding valve): pressure-limit valve 15,16 is only opened in case of a fault.Advantageously avoid thus: pollute the valve seat being configured to the pressure-limit valve 15,16 of seat valve.This dirt (pollution) can damage the closure function of pressure-limit valve 15,16.In valve in piston embodiment, pollution can not be anticipated.
Pressure-limit valve 15,16 is configured to pressure override valve, described pressure override valve such as when set by spring 21,22, the ultimate pressure of 4bar open.This ultimate pressure corresponds to the system pressure when opening sub-clutch, and described system pressure is kept by chip type spring prestressing force.
Relatively little ultimate pressure realizes the application of the Sealing of flexible relative.Thus, realize relatively large tolerance, the tolerance of such as +/-1bar, this corresponds to 25%.Electricity valve actuator 23,24 itself is not yet energized when this relatively low superpressure activation threshold value.When electric valve actuator 23,24 is energized, promote this superpressure activation threshold value, until exceed maximum system pressure.
Pressure-limit valve 15,16 can have been operated before pressure rising advantageously in hydrostatic circuit 11,12 by the control electronic equipment with electric actuator 23,24.During decompression advantageously in hydrostatic circuit 11,12, just again cancel the electricity operation of device 23,24.Advantageously realized by control strategy: pressure-limit valve 15,16 is never opened in double clutch system 10 normally runs.
Shown by a rectangle represented and two symbols 31,32 in fig. 2: two pressure-limit valves 25,26 also can be combined in common control valve unit 27.
By the suitable guiding of the circuit pilot line between the master cylinder that is connected to each other via hydrostatic circuit 11,12 and slave cylinder, common control valve unit 27 for maintaining valve can be configured to, an only valve of these two pilot line of the sub-clutch by double clutch can be operated.This advantage provided is: as shown by symbol 31,32 in Fig. 2, only needs a spring and an electric valve actuator.In addition, common control valve unit 27 is only connected with a bank 28.
According to a further aspect in the invention, electric actuator 23,24; 32 are configured for operating pressure-limit valve 15,16 as piezo actuator; 25,26 or 27.The advantage that piezo actuator provides is: it only must be energized under final controlling element is in tension force fully.
The pressure-limit valve 40 according to device 42 of the present invention had for providing additional pressure-reducing function is shown in figures 3 and 4 simplifiedly.Device 42 comprises the pressure-reduction outlet 44 in the valve chest 45 of pressure-limit valve 40.
Can by low for the decompression pressure in low pressure range or in reduction liquid-storage container via pressure-reduction outlet 44, described liquid-storage container is loaded with low pressure or external pressure.Valve chest 45 also comprises and enters opening 46, enters on opening described in system pressure is applied to.System pressure is such as downforce, one of described pressure hydrostatic circuit 11,12 being arranged in the hydraulic system shown in Fig. 1 and 2.
Valve chest 45 comprises receiving cavity 48, and in described receiving cavity, valve piston 50 is can reciprocating mode hold.In a similar fashion, valve piston 50 is equipped with two Sealings 51,52 to be similar in the mode of the master cylinder with vent.Sealing 51,52 is axially fixed in valve chest 45.
At this, Sealing 51,52 is configured to annular seal, and described annular seal has sealing lip in inner radial, and described sealing lip reclines valve piston 50 as seen in Figure 3.Sealing 51,52 in axial direction gauge annular chamber 53, described annular chamber in inner radial by valve piston 50 gauge.At radially outer, annular chamber 53 is by valve chest 45 gauge.Pressure-reduction outlet 44 starts from described annular chamber 53.
Valve piston 50 is by closing spring 55 pretension in the operating position that it is shown in Figure 3.In operating position, valve piston 50 is with the upper end portion backstop in its Fig. 3 and 4 on closed blocked part 56, and described closed blocked part is formed on valve chest 45.At this, closing spring 55 is supported on to be opened on blocked part 58, described in open blocked part and be arranged on equally on valve chest 45.Valve piston 50 can in the axial direction, i.e. to-and-fro motion between these two blocked parts 56 and 58 up and down in figures 3 and 4.
In operating position shown in Figure 3, pressure-reduction outlet 44 closed by piston valve 50.In the diagram, valve piston 50 shown in the open position of valve piston.In described open position, valve piston is released in the connection entered between opening 46 and pressure-reduction outlet 44, makes it possible to reduce pressure via pressure-reduction outlet 44, as shown by arrow 59 in the diagram.
Valve piston 50 is by the operation of final controlling element 60 electricity.When being energized to final controlling element 60, by final controlling element 60, Fig. 3 and 4 middle fingers power are upward applied on valve piston 50.This power acts on being additional to the closing force of closing spring 55.
When final controlling element 60 accesses in cold mode, so power is not applied on valve piston 50 by final controlling element 60.Under the cold state of final controlling element 60, valve piston 50 is tightened in its operating position consumingly in advance by closing spring 55, make valve piston 50 recline regularly closed blocked part 56 and close pressure-reduction outlet 44.
When entering opening 46 place's pressure increase, valve piston 50 must be remained on closed blocked part 56 by additional power on one's own initiative by the final controlling element 60 of energising.When a failure occurs, the system pressure entering opening 46 place is enough to open valve piston 50 through pressure-reduction outlet 44, and system pressure can be declined extremely rapidly.Opening blocked part 58 protects pressure-limit valve 40 from following impact: valve piston 50 moves downwardly to and hydraulic medium can be discharged at Sealing 52 place of bottom.
When pressure-limit valve 40 according to the present invention runs, final controlling element 60 can be accessed in cold mode when the system pressure entering opening 46 place is high to diagnose, declining via pressure drop opening 44 to check that whether pressure is as desired.When valve piston 50 is fixing, this can be stored in the fault memorizer of control apparatus and to show.
Reference numerals list
10 double clutch systems
11 hydrostatic circuits
12 hydrostatic circuits
15 pressure-limit valves
16 pressure-limit valves
17 banks
18 banks
21 symbols
22 symbols
23 symbols
24 symbols
25 pressure-limit valves
26 pressure-limit valves
27 control valve units
28 banks
31 symbols
32 symbols
40 pressure-limit valves
42 devices
44 pressure-reduction outlets
45 valve chests
46 enter opening
48 receiving cavities
50 valve pistons
51 Sealings
52 Sealings
53 annular chambers
55 closing springs
56 closed blocked parts
58 open blocked part
59 arrows
60 final controlling element
Claims (10)
1. have a hydraulic system for pressure-limit valve (40), described pressure-limit valve has ultimate pressure, and described ultimate pressure can improve by operating,
It is characterized in that, described pressure-limit valve (40) with for providing the device (42) of additional pressure-reducing function to combine.
2. hydraulic system according to claim 1, is characterized in that, described for providing the device (42) of additional pressure-reducing function to have pressure-reduction outlet (44).
3. hydraulic system according to claim 2, is characterized in that, described pressure-reduction outlet (44) is arranged between two Sealings (51,52).
4. the hydraulic system according to Claims 2 or 3, is characterized in that, described pressure-reduction outlet (44) can pass through valve piston (50) and close.
5. hydraulic system according to claim 4, is characterized in that, described valve piston (50) is tightened in operating position in advance by closing spring (55), and described in described operating position, pressure-reduction outlet (44) is closed.
6. hydraulic system according to claim 5, it is characterized in that, final controlling element (60) is attached troops to a unit in described valve piston (50), and described valve piston (50) is held in the operating position of valve piston by means of additional trying hard to keep by described final controlling element.
7. the hydraulic system according to any one of claim 4 to 6, it is characterized in that, described valve piston (50) in closed blocked part (56) and can open to-and-fro motion between blocked part (58), described blocked part of opening limits open position, and described in described open position, pressure-reduction outlet (44) is discharged by described valve piston (50).
8. the hydraulic system according to any one of the claims, is characterized in that, described pressure-limit valve (40) is attached troops to a unit in cut-off clutch, and described cut-off clutch is by the operation of hydrostatic clutch actuator.
9. hydraulic system according to any one of claim 1 to 8, is characterized in that, described pressure-limit valve (40) is attached troops to a unit in the hydrostatic circuit of the clutch system of hydrostatic operation.
10. one kind for running the method with the hydraulic system of pressure-limit valve (40) according to any one of the claims.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102013214428.8 | 2013-07-24 | ||
| DE102013214428 | 2013-07-24 | ||
| PCT/DE2014/200312 WO2015010696A2 (en) | 2013-07-24 | 2014-07-10 | Hydraulic system |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN105378298A true CN105378298A (en) | 2016-03-02 |
| CN105378298B CN105378298B (en) | 2017-11-17 |
Family
ID=51392021
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201480038144.4A Active CN105378298B (en) | 2013-07-24 | 2014-07-10 | Hydraulic system |
Country Status (3)
| Country | Link |
|---|---|
| CN (1) | CN105378298B (en) |
| DE (2) | DE102014213453A1 (en) |
| WO (1) | WO2015010696A2 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107940050A (en) * | 2016-10-12 | 2018-04-20 | 林德液压两合公司 | The pressure limiting valve of hydrostatic drive system |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2017174703A2 (en) | 2016-04-08 | 2017-10-12 | L'oreal | Process for manufacturing a false nail |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4815697A (en) * | 1988-04-22 | 1989-03-28 | General Electric Company | Depressurization valve |
| DE29807005U1 (en) * | 1998-04-18 | 1998-07-09 | Drägerwerk AG, 23558 Lübeck | Pressure relief valve for flowing media |
| US6234290B1 (en) * | 1998-08-06 | 2001-05-22 | Mannesmann Sachs Ag | Actuating installation for pneumatic clutch actuation with overload protection and/or incorrect-operation protection |
| CN1809697A (en) * | 2003-06-17 | 2006-07-26 | 奥特宁豪斯工厂有限责任公司 | Hydraulic circuit |
| CN201232669Y (en) * | 2008-07-30 | 2009-05-06 | 中江佳通印刷机械有限公司 | Single-single double hydraulic system for paper cutter |
Family Cites Families (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE3004581A1 (en) | 1980-02-08 | 1981-08-13 | Klöckner-Humboldt-Deutz AG, 5000 Köln | HYDROSTATIC CLUTCH |
| FI72931C (en) * | 1984-05-22 | 1987-08-10 | Valmet Oy | Damping valve for the clutch in a tractor's PTO shaft. |
| DE10293176D2 (en) * | 2001-07-19 | 2004-07-01 | Luk Lamellen & Kupplungsbau | Release system with parking lock function for controlling a clutch |
| CN101305197B (en) | 2005-11-11 | 2010-09-22 | 卢克摩擦片和离合器两合公司 | Method for the determination of a voltage limit of a clutch actuating motor |
| KR102198076B1 (en) | 2011-02-23 | 2021-01-05 | 섀플러 테크놀로지스 아게 운트 코. 카게 | Hydraulic device for actuating a clutch |
-
2014
- 2014-07-10 CN CN201480038144.4A patent/CN105378298B/en active Active
- 2014-07-10 WO PCT/DE2014/200312 patent/WO2015010696A2/en active Application Filing
- 2014-07-10 DE DE102014213453.6A patent/DE102014213453A1/en not_active Withdrawn
- 2014-07-10 DE DE112014003435.5T patent/DE112014003435B4/en active Active
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4815697A (en) * | 1988-04-22 | 1989-03-28 | General Electric Company | Depressurization valve |
| DE29807005U1 (en) * | 1998-04-18 | 1998-07-09 | Drägerwerk AG, 23558 Lübeck | Pressure relief valve for flowing media |
| US6234290B1 (en) * | 1998-08-06 | 2001-05-22 | Mannesmann Sachs Ag | Actuating installation for pneumatic clutch actuation with overload protection and/or incorrect-operation protection |
| CN1809697A (en) * | 2003-06-17 | 2006-07-26 | 奥特宁豪斯工厂有限责任公司 | Hydraulic circuit |
| CN201232669Y (en) * | 2008-07-30 | 2009-05-06 | 中江佳通印刷机械有限公司 | Single-single double hydraulic system for paper cutter |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107940050A (en) * | 2016-10-12 | 2018-04-20 | 林德液压两合公司 | The pressure limiting valve of hydrostatic drive system |
| CN107940050B (en) * | 2016-10-12 | 2022-02-18 | 林德液压两合公司 | Pressure limiting valve of hydrostatic drive system |
Also Published As
| Publication number | Publication date |
|---|---|
| WO2015010696A3 (en) | 2015-03-26 |
| WO2015010696A2 (en) | 2015-01-29 |
| DE102014213453A1 (en) | 2015-01-29 |
| DE112014003435A5 (en) | 2016-04-28 |
| DE112014003435B4 (en) | 2020-06-18 |
| CN105378298B (en) | 2017-11-17 |
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