CN101509510B - Hydraulic system - Google Patents
Hydraulic system Download PDFInfo
- Publication number
- CN101509510B CN101509510B CN 200810191085 CN200810191085A CN101509510B CN 101509510 B CN101509510 B CN 101509510B CN 200810191085 CN200810191085 CN 200810191085 CN 200810191085 A CN200810191085 A CN 200810191085A CN 101509510 B CN101509510 B CN 101509510B
- Authority
- CN
- China
- Prior art keywords
- hydraulic system
- pump
- stream
- switching
- cylinder
- 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.)
- Expired - Fee Related
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Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B7/00—Systems in which the movement produced is definitely related to the output of a volumetric pump; Telemotors
- F15B7/04—In which the ratio between pump stroke and motor stroke varies with the resistance against the motor
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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
- F15B7/00—Systems in which the movement produced is definitely related to the output of a volumetric pump; Telemotors
- F15B7/02—Systems with continuously-operating input and output apparatus
-
- 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
- F15B7/00—Systems in which the movement produced is definitely related to the output of a volumetric pump; Telemotors
- F15B7/06—Details
Abstract
The system has a master cylinder (1) and a slave cylinder (2), which are connected with each other by a hydraulic line (4). A pump (5) and a servo valve (18) are arranged in the line such that effect of an actuating force applied on the master cylinder is reinforced on the slave cylinder. An additional pump surge (12) with an input and an output, and a switching valve (40) i.e. 3/2 valve, are arranged in the line such that the effect of the actuating force is additionally reinforced on the slave cylinder based on a demand i.e. pedal speed.
Description
Technical field
The present invention relates to a kind of hydraulic system, in particular for Motor Vehicle, this hydraulic system has an active cylinder and a slave cylinder, this active cylinder and this slave cylinder are connected to each other by a hydraulic pressure section, in this hydraulic pressure section, be provided with a pump and a servovalve device like this, make the steering force be applied on this active cylinder strengthen the effect of this slave cylinder.
Background technique
By German laid-open document DE 10 2,005 041 419 A1 known a kind of hydraulic system, in this hydraulic system, the valve that can be called as servovalve has one first valve position and one second valve position, in this first valve position, active cylinder and slave cylinder are directly connected to each other to be connect, in this second valve position, active cylinder and slave cylinder are connected to each other by pump.By German laid-open document DE 10 2,005,056 442 A1 known a kind of similar hydraulic system, in this hydraulic system, be provided with an emergency opening mechanism that is used for clutch in the hydraulic pressure section between active cylinder and slave cylinder.
Summary of the invention
Task of the present invention is, a kind of hydraulic system that starts described type is provided, and this hydraulic system has long working life and can work inexpensively.
A kind of hydraulic system, in particular for Motor Vehicle, this hydraulic system has an active cylinder and a slave cylinder, this active cylinder and this slave cylinder are connected to each other by a hydraulic pressure section, in this hydraulic pressure section, be provided with a pump and a servovalve device like this, make the steering force be applied on the active cylinder strengthen to the effect of slave cylinder, in this hydraulic system, described task solves like this: in the hydraulic pressure section, be provided with a carried wet stream and the switching-valve arrangement with input end and output terminal like this, make be applied on the active cylinder steering force to the effect of slave cylinder with require relatively additionally enhancing.By with require relatively, especially connect carried wet stream relatively with pedal speed, can avoid hydraulic system to generate heat undesirably.In addition, by with require relatively, especially connect carried wet stream relatively with pedal speed, can significantly reduce the energy consumption of pump.
A preferred embodiment of this hydraulic system is characterised in that: switching-valve arrangement is connected between the input end and output terminal of carried wet stream like this, makes the output terminal of carried wet stream be connected with the input end of carried wet stream in first dislocation of switching-valve arrangement.In this dislocation, carried wet stream is carried by active cylinder circularly, wherein, only consumes less energy.
Another preferred embodiment of this hydraulic system is characterised in that: switching-valve arrangement is connected between the output terminal and slave cylinder of carried wet stream like this, makes the output terminal of carried wet stream be connected with slave cylinder in second dislocation of switching-valve arrangement.In this dislocation, carried wet stream makes steering force obtain additional the support, and especially the pedaling force by means of the automobile clutch of hydraulic system operation according to the present invention obtains additional the support.
Another preferred embodiment of this hydraulic system is characterised in that: switching-valve arrangement is by a hydraulic pressure impedor control.By producing pressure reduction in the volume flow of hydraulic pressure impedor between slave cylinder and active cylinder.
Another preferred embodiment of this hydraulic system is characterised in that: switching-valve arrangement comprises a changing valve piston, and this changing valve piston is loaded the pressure of hydraulic pressure impedor front and the pressure of back thereof.Switching-valve arrangement is preferably configured as two position three way directional control valve, and the changing valve piston of this two position three way directional control valve is by the control of hydraulic pressure impedor.
Another preferred embodiment of this hydraulic system is characterised in that: an end of changing valve piston is additionally loaded by the pre-tensioning of a spring.By spring the preferred precompressed of changing valve piston is tightened in such dislocation: in this dislocation, carried wet stream is carried circularly.
Another preferred embodiment of this hydraulic system is characterised in that: the hydraulic pressure impedor is connected the back of active cylinder.Preferred hydraulic pressure impedor is set directly at the back of active cylinder.
Another preferred embodiment of this hydraulic system is characterised in that: the hydraulic pressure impedor comprises a flow controller.Flow controller is preferably configured as the volume flowrate flow controller.
Another preferred embodiment of this hydraulic system is characterised in that: the servovalve device is connected with pump like this, makes one can discharge different servovalve opening cross-section by servo valve piston reciprocating in the servovalve housing, that bear initial spring tension.For example being connected in German laid-open document DE 10 2,005 041 419 A1 of servovalve device and pump, especially open in Fig. 3 and Fig. 4 and in affiliated description of drawings.
Another preferred embodiment of this hydraulic system is characterised in that: pump comprises first pump stream and carried wet stream, and this carried wet stream can be connected with first pump stream.Scheme as an alternative, these two pumps streams also can be provided by two pumps that can be coupled each other.
Description of drawings
From the explanation that with reference to the accompanying drawings embodiment is described in detail, obtain other advantage of the present invention, feature and details.Accompanying drawing is represented:
Fig. 1 is according to the hydraulic circuit diagram of hydraulic system of the present invention, and changing valve is in the primary importance; And
Hydraulic circuit diagram among Fig. 2 Fig. 1, changing valve is in the second place.
Embodiment
A hydraulic system that is used for the servo support of operated clutch has been shown among Fig. 1 and Fig. 2.Reduce the pedaling force that automobile driver is felt by servo support.This hydraulic system comprises an only schematically illustrated active cylinder 1, and this active cylinder is operated by (unshowned) clutch pedal.Active cylinder 1 is in slave cylinder 2 by a hydraulic pressure section 4 that is provided with pump 5 and is connected this slave cylinder and the acting in conjunction of (unshowned) clutch release assembly.
According to a main aspect of the present invention, pump 5 comprises two pump streams 11,12, and the input end of these pump streams is connected on the connecting pipeline 14, and this connecting pipeline is in slave cylinder 2 and with active cylinder 1 and is connected.The output terminal of pump stream 11 is in connecting pipeline 14 by bypass line 15 and is connected.Bypass line 15 leads in the connecting pipeline 14 on branching portion 16.Between the input end of branching portion 16 and first pump stream 11, be connected with a main valve 18.
An other bypass line 23 extends between line branching portion 21 and pipeline cross part 22, is provided with a safety valve 24 in this other bypass line, and this safety valve structure becomes safety check.Line branching portion 21 is arranged between slave cylinder 2 and the branching portion 16.Between branching portion 16 and pipeline cross part 22, from branching portion 16, the input end of main valve 18, first pump stream 11 and the input end of second pump stream 12 are connected on the connecting pipeline 14.Described other bypass line 23 cross-over connection pumps flow 11,12 input end and main valve 18.Dashed rectangle 25 frames go into one with German laid-open document DE 10 2,005 041419 A1 in the similar subtense angle of disclosed subtense angle.
Changing valve 40 comprises a changing valve housing, but changing valve piston 42 to-and-fro motion be received in this changing valve housing.Changing valve piston 42 is loaded by the pre-tensioning of spring 44 on an end.Changing valve piston 42 is loaded the pressure of measuring flow controller 34 fronts by pilot line 35 on same end.Changing valve piston 42 is loaded the pressure of measuring flow controller 34 back by described other pilot line 36 on its opposite end, be loaded in other words to measure the pressure that produces between flow controller 34 and the active cylinder 1.
On changing valve 40, be connected with three connecting end pipelines 45,46,47.Connecting end pipeline 45 makes changing valve 40 be connected with the output terminal of carried wet stream 12, and this carried wet stream is also referred to as second pump stream.Connecting end pipeline 46 carries out the transition to connecting pipeline 14, and it makes pipeline cross part 22 be connected with changing valve 40.Connecting end pipeline 47 leads in the connecting pipeline 14 on an other branching portion 49.Branching portion 49 is arranged between two branching portions 16 and 21.
In dislocation shown in Fig. 1 of changing valve 40, second pump stream 12 is transported in the connecting pipeline 14 via connecting end pipeline 45,46, promptly is transported to the input end of second pump stream 12.Realize that thus second pump stream 12 only needs less energy.
In dislocation shown in Fig. 2 of changing valve 40, the pedaling force support that second pump stream 12 is transported to slave cylinder 2 and can realizes thus adding via connecting end pipeline 45 and 47.
The conversion of changing valve 40 or operation by being preferably configured as the volume flowrate flow controller measurement flow controller 34 and control by pedal speed thus, active cylinder 1 is with this pedal speed action.If pedal speed and then surpass the threshold value of determining by the volume flowrate of measuring flow controller 34, the pressure reduction of then measuring flow controller 34 places reaches the conversion boundary of changing valve 40.When transfer speed is low relatively, occupy dislocation shown in Fig. 1 of changing valve 40, when pedal speed is high relatively, occupy dislocation shown in Fig. 2 of changing valve 40.
The reference number inventory
1 active cylinder, 2 slave cylinders
4 hydraulic pressure sections 28 are pipeline initiatively
5 pumps, 31 branch parts
11 pumps flow 32 branch parts
12 pumps stream 34 is measured flow controller
14 connecting pipelines 35 are pipeline initiatively
15 bypass lines 36 are pipeline initiatively
16 branching portions, 40 changing valves
18 main valves, 42 changing valve pistons
21 line branching portions, 44 springs
22 pipeline cross parts, 45 connecting end pipelines
23 bypass lines, 46 connecting end pipelines
24 safety valves, 47 connecting end pipelines
25 rectangles, 49 branching portions
Claims (8)
1. hydraulic system, be used for Motor Vehicle, this hydraulic system has an active cylinder (1) and a slave cylinder (2), this active cylinder and this slave cylinder are connected to each other by a hydraulic pressure section (4), in this hydraulic pressure section, be provided with a pump (5) and a servovalve device (18) like this, make the steering force be applied on this active cylinder (1) strengthen to the effect of this slave cylinder (2), it is characterized in that: in this hydraulic pressure section (4), be provided with carried wet stream (12) and a switching-valve arrangement (40) with input end and output terminal like this, make be applied on this active cylinder (1) steering force to the effect of this slave cylinder (2) with require relatively additionally enhancing;
Wherein, switching-valve arrangement (40) is connected between the input end and output terminal of this carried wet stream (12) like this, makes the output terminal of this carried wet stream (12) be connected with the input end of this carried wet stream (12) in first dislocation of this switching-valve arrangement (40); And
This switching-valve arrangement (40) is connected between the output terminal and this slave cylinder (2) of this carried wet stream (12) like this, makes the output terminal of this carried wet stream (12) be connected with this slave cylinder (2) in second dislocation of this switching-valve arrangement (40).
2. hydraulic system according to claim 1 is characterized in that: this switching-valve arrangement (40) is by a hydraulic pressure impedor (34) control.
3. hydraulic system according to claim 2 is characterized in that: this switching-valve arrangement (40) comprises a changing valve piston (42), and this changing valve piston is loaded the pressure of this hydraulic pressure impedor (34) front and the pressure of back thereof.
4. hydraulic system according to claim 3 is characterized in that: an end of this changing valve piston (42) is additionally loaded by the pre-tensioning of a spring (44).
5. according to the described hydraulic system of one of claim 2 to 4, it is characterized in that: this hydraulic pressure impedor (34) is connected the back of this active cylinder (1).
6. according to the described hydraulic system of one of claim 2 to 4, it is characterized in that: this hydraulic pressure impedor (34) comprises a flow controller.
7. according to the described hydraulic system of one of aforementioned claim 1-4, it is characterized in that: this servovalve device (18) is connected with this pump (5) like this, makes one can discharge different servovalve opening cross-section by servo valve piston reciprocating in the servovalve housing, that bear initial spring tension.
8. according to the described hydraulic system of one of aforementioned claim 1-4, it is characterized in that: this pump (5) comprises one first pump stream (11) and this carried wet stream (12), and this carried wet stream can be connected with this first pump stream (11).
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102007061268.2 | 2007-12-19 | ||
| DE102007061268 | 2007-12-19 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN101509510A CN101509510A (en) | 2009-08-19 |
| CN101509510B true CN101509510B (en) | 2013-07-31 |
Family
ID=40690211
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 200810191085 Expired - Fee Related CN101509510B (en) | 2007-12-19 | 2008-12-19 | Hydraulic system |
Country Status (2)
| Country | Link |
|---|---|
| CN (1) | CN101509510B (en) |
| DE (1) | DE102008059787A1 (en) |
Families Citing this family (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102013006047A1 (en) * | 2013-04-06 | 2014-10-09 | GM Global Technology Operations, LLC (n.d. Ges. d. Staates Delaware) | Throttle valve for a hydraulic clutch actuator |
| DE102014220073A1 (en) | 2014-10-02 | 2016-04-07 | Schaeffler Technologies AG & Co. KG | clutch release |
| DE102015205858A1 (en) | 2015-04-01 | 2016-10-06 | Schaeffler Technologies AG & Co. KG | Clutch actuation system |
| DE102015205850A1 (en) | 2015-04-01 | 2016-10-06 | Schaeffler Technologies AG & Co. KG | Clutch actuation system |
| DE102015207088A1 (en) | 2015-04-20 | 2016-10-20 | Schaeffler Technologies AG & Co. KG | Clutch actuation system |
| DE102015219661A1 (en) | 2015-10-12 | 2017-04-13 | Schaeffler Technologies AG & Co. KG | Clutch actuation system |
| DE102016213319A1 (en) | 2016-07-21 | 2018-01-25 | Schaeffler Technologies AG & Co. KG | fluid arrangement |
| DE102016219153A1 (en) | 2016-10-04 | 2018-04-05 | Schaeffler Technologies AG & Co. KG | Clutch actuation system |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1653272A (en) * | 2002-05-14 | 2005-08-10 | 卢克摩擦片和离合器两合公司 | Hydraulisches system |
| EP1857703A1 (en) * | 2006-05-17 | 2007-11-21 | LuK Lamellen und Kupplungsbau Beteiligungs KG | Method for actuating an electrical motor of a hydrostatic pump in a hydraulic system |
Family Cites Families (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP1635071A2 (en) * | 2004-09-11 | 2006-03-15 | LuK Lamellen und Kupplungsbau Beteiligungs KG | Hydraulic system, especially for vehicles |
| DE102005041419B4 (en) | 2004-09-11 | 2015-07-16 | Schaeffler Technologies AG & Co. KG | Hydraulic system, in particular for motor vehicles |
| DE102005056442A1 (en) | 2004-12-22 | 2006-07-06 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Hydraulic system for use in vehicle, has emergency release mechanism including leakage sites, and hydraulic circuits communicating with one another in mutually controllable fashion via valve block |
| EP1674736A3 (en) * | 2004-12-22 | 2009-06-03 | LuK Lamellen und Kupplungsbau Beteiligungs KG | Hydraulic system for power assisted clutch actuation comprising an emergency release mechanism |
-
2008
- 2008-12-01 DE DE102008059787A patent/DE102008059787A1/en not_active Withdrawn
- 2008-12-19 CN CN 200810191085 patent/CN101509510B/en not_active Expired - Fee Related
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1653272A (en) * | 2002-05-14 | 2005-08-10 | 卢克摩擦片和离合器两合公司 | Hydraulisches system |
| EP1857703A1 (en) * | 2006-05-17 | 2007-11-21 | LuK Lamellen und Kupplungsbau Beteiligungs KG | Method for actuating an electrical motor of a hydrostatic pump in a hydraulic system |
Also Published As
| Publication number | Publication date |
|---|---|
| DE102008059787A1 (en) | 2009-06-25 |
| CN101509510A (en) | 2009-08-19 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| ASS | Succession or assignment of patent right |
Owner name: LUK VERMOEGENSVERWALTUNGSGESELLSCHAFT MBH Free format text: FORMER OWNER: LUK LAMELLEN UND KUPPLUNGSBAU GMBH Effective date: 20130618 Owner name: SCHAEFFLER TECHNOLOGY GMBH + CO. KG Free format text: FORMER OWNER: LUK VERMOEGENSVERWALTUNGSGESELLSCHAFT MBH Effective date: 20130618 |
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| C41 | Transfer of patent application or patent right or utility model | ||
| TA01 | Transfer of patent application right |
Effective date of registration: 20130618 Address after: German Herzogenaurach Applicant after: SCHAEFFLER TECHNOLOGIES AG & CO. KG Address before: German Boer Applicant before: Luke Asset Management Co.,Ltd. Effective date of registration: 20130618 Address after: German Boer Applicant after: Luke Asset Management Co.,Ltd. Address before: German Boer Applicant before: LUK LAMELLEN UND KUPPLUNGSBAU BETEILIGUNGS KG |
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| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20130731 Termination date: 20191219 |