WO1990012217A1 - Clutch actuating hydraulic circuit - Google Patents
Clutch actuating hydraulic circuit Download PDFInfo
- Publication number
- WO1990012217A1 WO1990012217A1 PCT/JP1990/000262 JP9000262W WO9012217A1 WO 1990012217 A1 WO1990012217 A1 WO 1990012217A1 JP 9000262 W JP9000262 W JP 9000262W WO 9012217 A1 WO9012217 A1 WO 9012217A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- clutch
- hydraulic
- pressure
- switching valve
- circuit
- Prior art date
Links
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
- 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
- F16H61/0021—Generation or control of line pressure
- F16H61/0025—Supply of control fluid; Pumps therefore
-
- 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
- F16D25/00—Fluid-actuated clutches
- F16D25/12—Details not specific to one of the before-mentioned types
- F16D25/14—Fluid pressure control
-
- 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
-
- 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
-
- 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
- F16D48/04—Control by fluid pressure providing power assistance
-
- 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
- F16D2048/0227—Source of pressure producing the clutch engagement or disengagement action within a circuit; Means for initiating command action in power assisted devices
- F16D2048/0233—Source of pressure producing the clutch engagement or disengagement action within a circuit; Means for initiating command action in power assisted devices by rotary pump actuation
- F16D2048/0236—Source of pressure producing the clutch engagement or disengagement action within a circuit; Means for initiating command action in power assisted devices by rotary pump actuation with multiple independent pumps, e.g. one per clutch, or for supplying fluid to different systems
- F16D2048/0242—Two or more rotating pumps driven together by the same power source, e.g. connected by a shaft, or a single pump having two or more fluid outputs
-
- 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
- F16D2048/0257—Hydraulic circuit layouts, i.e. details of hydraulic circuit elements or the arrangement thereof
- F16D2048/0272—Two valves, where one valve is supplying fluid to the cylinder and the other valve is for draining fluid to the sump
-
- 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
- F16D2500/00—External control of clutches by electric or electronic means
- F16D2500/30—Signal inputs
- F16D2500/316—Other signal inputs not covered by the groups above
- F16D2500/3166—Detection of an elapsed period of time
Definitions
- the present invention relates to a clutch operating hydraulic surface, and more particularly to a clutch operating hydraulic surface suitable for reducing the output loss of the clutch operating hydraulic surface.
- the clutch is roughly divided into the type in which the hydraulic pressure acts and the clutch engages (therefore, when the hydraulic pressure stops acting, the clutch separates).
- Two types a type in which the clutch releases when hydraulic pressure acts (accordingly, a type in which the clutch engages when the hydraulic pressure stops acting).
- the hydraulic circuit for operating the clutch is divided into the same hydraulic hydraulic circuit for operating the clutch without changing its configuration. It can support any of the clutch types. This is because, even if the clutch type has changed, it is only necessary to change the way of reading or reading the hydraulic surface for operating the clutch. Specifically, the explanation will be made based on the conventional hydraulic surface for clutch operation shown in FIG.
- the position 6A of the switching valve 6 indicates the clutch engagement position, and the position 6B indicates the clutch release position. Conversely, the clutch is the latter type. In the formula, the position 6A indicates the clutch release position, and the position 6B indicates the clutch engagement position.
- the description will be made on the basis of the former clutch type hydraulic circuit for operating the clutch.
- the above-mentioned conventional hydraulic surface for clutch operation has the following problems.
- the discharge flow rate of the hydraulic pump required for operating the hydraulic actuator is determined by the displacement of the hydraulic actuator and the operating time of the hydraulic actuator. If this is applied to the hydraulic surface for operating the clutch, the Once the engagement is completed, all of the discharge flow rate of the hydraulic pump 2 is unnecessary except to compensate for the leakage of the hydraulic circuit for operating the clutch. become .
- the conventional hydraulic surface for operating the clutch requires that the discharge oil be raised to the set pressure of the pressure limiting valve 5 even after the clutch 7 has been engaged. Then, it is configured to be returned to the oil reservoir 1.
- the present invention has been made in view of the above-described conventional problems, and has as its object to provide a hydraulic surface for operating a clutch, which is well-known for reducing unnecessary output loss. Yes. Disclosure of the invention
- the present invention provides a clutch having a switching valve in a pressure surface between a hydraulic pump and a clutch, and having a pressure limiting valve between a reflux surface of the valve and the pressure surface.
- the other hydraulic pump and the switching valve that switches the discharge oil of this pump are connected.
- the downstream circuit of the switching valve is a hydraulic circuit connected to the pressure circuit and the return surface circuit.
- a throttle is provided in the pressure circuit, and a switching valve for switching between a downstream side surface of the pressure circuit and a discharge oil of another hydraulic pump is surrounded by a pipe opening surface.
- a throttle is provided in the EI path on the downstream side of the pressure limiting valve instead of the pressure surface, and the switching valve on the upstream side thereof is connected by a pilot circuit.
- the switching valve for switching the discharge oil of another hydraulic pump is an electromagnetic switching valve that switches between an electromagnet and a timer.
- the clutch has the configuration of the former type described in the conventional technology, when the clutch is engaged (when the clutch is completely engaged, the following will be described).
- the discharge oil from the hydraulic pumps joins and is guided to the clutch, which acts to increase the engagement speed of the clutch.
- the other hydraulic pumps will simply be refilled. It may be a small capacity hydraulic pump for use, or just the output it drives. In other words, when the clutch is engaged, the output required for the clutch engagement is generated, and when the clutch is not engaged, the required output is generated only at that time. Therefore, the output loss can be reduced for this purpose.
- FIG. 1 is a hydraulic circuit for clutch operation showing a first embodiment of the present invention
- FIG. 2 is a hydraulic circuit for clutch operation showing a second embodiment
- FIG. 3 is a third embodiment.
- An example of the hydraulic surface for clutch operation is shown in FIG. 4, and FIG. 4 shows a conventional hydraulic surface for clutch operation.
- BEST MODE FOR CARRYING OUT THE INVENTION An embodiment of a hydraulic surface for clutch operation according to the present invention will be described with reference to FIGS. 1 to 3.
- FIG. These hydraulic paths are based on the conventional hydraulic paths (FIG. 4), and the explanation of the clutch operation and the like will be omitted.
- the hydraulic surfaces of these embodiments are of a type in which the clutch is engaged by hydraulic pressure, and one clutch is used.
- the pump was 2 mm. In each of these embodiments, these hydraulic pumps are driven by the same power source, and are denoted by 2a and 2b.
- the discharge oil from the hydraulic pump 2a reaches the switching valve 6 via the pressure surfaces 31 and 33.
- a pressure limiting valve 5 is mounted on the pressure path 31, and a junction path 32 is connected thereto.
- a pilot surface 34 for taking out pilot pressure is installed in the pressure surface 33, and a space is provided between these pressure surfaces 31 and 33. It has a diaphragm 41 attached.
- the merging surface 32 and the pilot surface 34 are connected to a switching valve 8.
- This switching valve 8 is a no-manipulation type 3 port 2 position, the upstream side is connected to the hydraulic pump 2b, and the downstream ffl is connected to the merging circuit 32 and the return surface 9 are doing .
- the discharge oil from the hydraulic pump 2b is connected to the recirculation surface 9 at the position 8A and to the junction surface 32 at the position 8B.
- This switching is performed by adjusting the balance between the magnitude of the pilot hydraulic pressure from the pilot pilot surface 34 and the panel 81 mounted on the switching valve 8. Is determined by If the pilot hydraulic pressure is greater than the biasing force of the piston 81, the position becomes 8A (the state shown in the figure), and conversely, the pilot hydraulic pressure becomes higher. If less than the biasing force, position 8B would be.
- This position 6 B is also connected to the return surface 9.
- the operation of the above configuration will be described below.
- the oil discharged from the hydraulic pump 2a is discharged while the switching valve 6 is closed (Fig. At the indicated position 6B), the pressure is regulated by the pressure limiting valve 5 and the pressure is returned to the oil reservoir 1.
- the switching valve 6 is operated and the oil passage to the clutch 7 is opened (the state shown in the figure)
- the piston 71 moves and the valve 71 is moved to the lower position.
- the oil pressure in the pressure surface 33 decreases due to the restriction of the pressure surface 31 by the throttle 41, and the pipe opening of the switching valve 8 decreases.
- the pressure 34 is lost to the panel 81, the switching valve 8 is switched to the position 8B, and the oil discharged from the hydraulic pump 2b is connected to the hydraulic pump 2a via the merging circuit 32.
- the moving speed of the business 71 is increased by the merging.
- the movement of the piston 71 stops, so that the oil pressure of the pressure circuit 33 approaches the set pressure of the pressure limiting valve 5.
- the pilot pressure 34 of the switching valve 8 beats the spring 81 and the switching valve 8 is switched to the position 8A shown in the same figure, and the hydraulic pump 2b is closed. Reflux oil to oil reservoir 1 with no load.
- the throttle 41 in the first embodiment and the cut-out surface 34 are eliminated, and the throttle 42 is replaced with a pressure limit. Installed on the downstream side of the valve 5 (return surface 9), the recirculation pressure is set upstream of the throttle 42.
- the throttle 41 in the first embodiment and the throttle surface 34 are completely abolished, and the switching valve 8 is omitted.
- It is an electromagnetic switching valve.
- the solenoid-operated switching valve 8 is switched by the electromagnet 82 at the same time as the switching of the switching valve 6, and the hydraulic pumps 2a and 2b are joined to engage the clutch. After a lapse of a certain period of time, the electromagnetic switching valve 8 is returned by a timer.
- the hydraulic surface for engaging the clutch by hydraulic pressure has been described, but the clutch can be disengaged by hydraulic pressure. Even in the case of a hydraulic circuit, the effect of reducing output loss can be obtained as in the above three embodiments.
- the present invention is suitable for reducing the output loss of the hydraulic surface for operating the clutch, and particularly, when the clutch is engaged (or disengaged), at least one hydraulic pump is discharged.
- the oil joins the discharge from other hydraulic pumps and reduces the output loss of the hydraulic surface for operating the clutch to increase the flow rate to the clutch. It is useful as a hydraulic surface for latch operation.
Description
Claims
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
KR1019910701223A KR920701708A (ko) | 1989-03-31 | 1990-02-28 | 클러치작동용 유압회로 |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP1/82965 | 1989-03-31 | ||
JP1082965A JPH02261930A (ja) | 1989-03-31 | 1989-03-31 | クラッチ作動用油圧回路 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO1990012217A1 true WO1990012217A1 (en) | 1990-10-18 |
Family
ID=13788939
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP1990/000262 WO1990012217A1 (en) | 1989-03-31 | 1990-02-28 | Clutch actuating hydraulic circuit |
Country Status (5)
Country | Link |
---|---|
US (1) | US5163542A (ja) |
EP (1) | EP0465650A4 (ja) |
JP (1) | JPH02261930A (ja) |
KR (1) | KR920701708A (ja) |
WO (1) | WO1990012217A1 (ja) |
Families Citing this family (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US5228289A (en) * | 1983-06-29 | 1993-07-20 | Peter Norton | Plural hydraulic pump system with unloading valve |
US5992599A (en) * | 1996-12-30 | 1999-11-30 | Ab Volvo Penta | Control system for intermittently pulsing a valve controlling forward and reverse clutches a transmission and transmission fitted therewith |
DE10056954A1 (de) * | 2000-11-17 | 2002-05-23 | Zf Sachs Ag | Kupplungssystem |
US6932583B2 (en) * | 2001-04-16 | 2005-08-23 | Siemens Diesel Systems Technology | Multiple stage pump with multiple external control valves |
WO2005064187A1 (de) * | 2003-12-09 | 2005-07-14 | Gkn Driveline International Gmbh | Hydrauliksystem für zwei lamellenkupplungen |
DE102004033439C5 (de) * | 2004-07-08 | 2009-02-26 | Getrag Driveline Systems Gmbh | Antriebsstrang für ein Kraftfahrzeug |
FR2950400B1 (fr) * | 2009-09-23 | 2011-09-30 | Equip Manutention Et Transp Soc D | Circuit hydraulique a plusieurs configurations, application a un camion-benne, et camion-benne utilisant un tel circuit. |
DE102015225301A1 (de) * | 2015-12-15 | 2017-06-22 | Zf Friedrichshafen Ag | Hydraulische Betätigung einer Kupplung |
Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS55115605A (en) * | 1979-02-26 | 1980-09-05 | Komatsu Ltd | Flow distributing valve |
JPS55132402U (ja) * | 1979-03-13 | 1980-09-19 | ||
JPS5829643A (ja) * | 1981-08-17 | 1983-02-21 | Japan Steel Works Ltd:The | 射出成形機の油量切換装置 |
Family Cites Families (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE1031648B (de) * | 1952-10-22 | 1958-06-04 | Borg Warner | Schaltvorrichtung fuer eine Kraftfahrzeugkupplung |
US3809201A (en) * | 1970-10-30 | 1974-05-07 | Kobe Steel Ltd | Modulating valve for vehicle transmission systems |
US3985063A (en) * | 1974-08-30 | 1976-10-12 | Borg-Warner Corporation | Hydraulic control system |
JPS6048249B2 (ja) * | 1977-08-29 | 1985-10-26 | 住友重機械工業株式会社 | 金型予熱用の金型離隔装置 |
JPS55132402A (en) * | 1979-03-30 | 1980-10-15 | Kayaba Ind Co Ltd | Position control valve |
JPS57154503A (en) * | 1981-03-13 | 1982-09-24 | Jidosha Kiki Co Ltd | Pressurized fluid feeder |
JPS5935771A (ja) * | 1982-08-24 | 1984-02-27 | 共和眞空技術株式会社 | 真空凍結乾燥装置のトラツプの除霜再生方法と装置 |
JPS60101324A (ja) * | 1983-11-07 | 1985-06-05 | Yanmar Diesel Engine Co Ltd | 油圧クラツチ装置 |
JPS61140621A (ja) * | 1984-12-12 | 1986-06-27 | Mitsuwa Seiki Co Ltd | クラツチ操作機構 |
-
1989
- 1989-03-31 JP JP1082965A patent/JPH02261930A/ja active Pending
-
1990
- 1990-02-28 EP EP19900903924 patent/EP0465650A4/en not_active Ceased
- 1990-02-28 US US07/762,010 patent/US5163542A/en not_active Expired - Fee Related
- 1990-02-28 KR KR1019910701223A patent/KR920701708A/ko not_active Application Discontinuation
- 1990-02-28 WO PCT/JP1990/000262 patent/WO1990012217A1/ja not_active Application Discontinuation
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS55115605A (en) * | 1979-02-26 | 1980-09-05 | Komatsu Ltd | Flow distributing valve |
JPS55132402U (ja) * | 1979-03-13 | 1980-09-19 | ||
JPS5829643A (ja) * | 1981-08-17 | 1983-02-21 | Japan Steel Works Ltd:The | 射出成形機の油量切換装置 |
Non-Patent Citations (1)
Title |
---|
See also references of EP0465650A4 * |
Also Published As
Publication number | Publication date |
---|---|
EP0465650A1 (en) | 1992-01-15 |
JPH02261930A (ja) | 1990-10-24 |
EP0465650A4 (en) | 1992-01-22 |
KR920701708A (ko) | 1992-08-12 |
US5163542A (en) | 1992-11-17 |
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