WO2011026458A1 - Hydraulikanordnung mit einer doppelt wirkenden hydraulikvorrichtung - Google Patents
Hydraulikanordnung mit einer doppelt wirkenden hydraulikvorrichtung Download PDFInfo
- Publication number
- WO2011026458A1 WO2011026458A1 PCT/DE2010/000958 DE2010000958W WO2011026458A1 WO 2011026458 A1 WO2011026458 A1 WO 2011026458A1 DE 2010000958 W DE2010000958 W DE 2010000958W WO 2011026458 A1 WO2011026458 A1 WO 2011026458A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- hydraulic
- piston
- fluid path
- hydraulic cylinder
- cylinder
- Prior art date
Links
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
- F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
- F15B21/04—Special measures taken in connection with the properties of the fluid
- F15B21/044—Removal or measurement of undissolved gas, e.g. de-aeration, venting or bleeding
-
- 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
- F16H61/26—Generation or transmission of movements for final actuating mechanisms
- F16H61/28—Generation or transmission of movements for final actuating mechanisms with at least one movement of the final actuating mechanism being caused by a non-mechanical force, e.g. power-assisted
- F16H61/30—Hydraulic or pneumatic motors or related fluid control means therefor
-
- 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
- F16H63/00—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism
- F16H63/02—Final output mechanisms therefor; Actuating means for the final output mechanisms
- F16H63/30—Constructional features of the final output mechanisms
- F16H63/3023—Constructional features of the final output mechanisms the final output mechanisms comprising elements moved 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
- 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
- F16H2061/004—Venting trapped air from hydraulic systems
-
- 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
- F16H61/26—Generation or transmission of movements for final actuating mechanisms
- F16H61/28—Generation or transmission of movements for final actuating mechanisms with at least one movement of the final actuating mechanism being caused by a non-mechanical force, e.g. power-assisted
- F16H61/30—Hydraulic or pneumatic motors or related fluid control means therefor
- F16H2061/307—Actuators with three or more defined positions, e.g. three position servos
Definitions
- the invention relates to a hydraulic arrangement with a double-acting hydraulic device, by means of which in particular a gear selection of a transmission is actuated, wherein the hydraulic device is a hydraulic cylinder, a hydraulic cylinder associated with the first hydraulic access by means of which the hydraulic cylinder can be acted upon by a hydraulic medium, a hydraulic cylinder associated with the second hydraulic access means the hydraulic cylinder is acted upon by the hydraulic medium and a displaceably mounted within the hydraulic cylinder between the hydraulic ports reciprocally hydraulic piston which divides the hydraulic cylinder into two piston chambers has.
- Hydraulic arrangements with a double-acting hydraulic device are known. They can be used as adjusting cylinders or gear regulators in automatic transmissions, such as stepped automatic transmissions, CVT transmissions or dual-clutch transmissions.
- Hydraulic systems usually contain more or less foamed oil.
- the dissolved or undissolved air can settle in the piston chamber of the hydraulic cylinder in the form of an air bubble.
- the air bubble When applying pressure, the air bubble must be compressed accordingly and thus oil volume nachgeAppt. On the one hand, this can lead to dynamic deterioration as well as to pressure peaks or vibrations. Air in the hydraulic system also affects the rigidity of the system and thus its damping.
- the object of the present invention is to improve the venting of a piston chamber of a hydraulic cylinder, in particular to minimize leakage and / or efficiency losses.
- the object is in a hydraulic arrangement with a double-acting hydraulic device, by means of which in particular a gear selection of a transmission is actuated, wherein the hydraulic device is a hydraulic cylinder, a hydraulic cylinder associated with the first hydraulic access by means of which the hydraulic cylinder is acted upon by a hydraulic medium, a hydraulic cylinder associated second hydraulic access by means of which the hydraulic cylinder with the hydraulic medium can be acted upon and displaceable within the hydraulic cylinder between the hydraulic inputs reciprocally mounted hydraulic piston which divides the hydraulic cylinder into two piston chambers, characterized in that a fluid path, at least in a central position of the hydraulic piston, the piston chambers with each other is provided connects.
- any air present in the piston chambers can pass from one piston chamber into the other piston chamber. This can be done advantageously shortly after or during a control for moving out of the hydraulic piston from a middle position.
- one of the piston chambers is pressurized and the other piston chamber is depressurized, for example, assigned to a tank of the hydraulic system.
- the air located in the pressurized piston chamber can be transported very quickly and efficiently into the non-pressurized piston chamber.
- the then located in the non-pressurized piston chamber air emptied together with the hydraulic medium contained therein in the tank.
- an automatic ventilation of the respectively hydraulically energized piston chamber can take place during each adjusting movement from the middle position.
- a permanent leakage at applied pressure and a loss of efficiency associated therewith, as would occur, for example, in a direct venting connection can thereby be avoided.
- the fluid path has a throttle and / or a diaphragm and / or a hydraulic resistance.
- the hydraulic resistance, the throttle and / or the diaphragm can be set so that any air volume present can be transported sufficiently quickly into the respective other piston chamber.
- the hydraulic medium is present at the hydraulic resistance, the diaphragm and / or the throttle, a comparatively small volume flow arises due to the greater density, which can advantageously be chosen so small that an actuating movement of the hydraulic piston does not or at least only insignificantly is impaired.
- the fluid path itself is designed and / or dimensioned such that it represents or realizes the hydraulic resistance.
- the fluid path connects two hydraulic ports which open into the hydraulic cylinder at a distance from one another and between the hydraulic ports.
- the fluid path can be positioned in the middle position of the hydraulic piston between the two spaced-apart hydraulic ports.
- the fluid path thus forms a bypass.
- the corresponding hydraulic muzzle can advantageously be closed by means of the hydraulic piston itself so that no secondary flow ceases to occur.
- the fluid path has at least one depression and / or groove and / or a groove running in a longitudinal direction of the hydraulic cylinder and / or a groove with a constriction.
- the fluid path can be realized by simply inserting the recess or the groove into an inner wall of the hydraulic cylinder.
- the bottleneck can realize the throttle, the aperture and / or the hydraulic resistance.
- a length of the recess and / or the groove may be selected so that the fluid path is only shorter than a Rescueverstellweg from the center position is effective over a certain adjustment. Once the hydraulic piston has covered the adjustment, the fluid path is automatically closed or is no longer effective.
- the distance of the hydraulic openings or a length of the groove is greater than a width of the hydraulic piston.
- the hydraulic piston can be bypassed in its center position.
- the fluid path in a first end position and / or in a second end position, is hydraulically short-circuited or shut off by means of the hydraulic piston.
- short-circuited it can be understood that an identical hydraulic pressure is present at one end and at a beginning of the fluid path, for example a corresponding hydraulic pressure of one of the piston chambers.
- the fluid path is no longer effective in the end position, so that Partial in the end position caused by the fluid path leakage can no longer occur.
- the hydraulic arrangement has a hydraulic energy source for providing the hydraulic medium and a pressureless tank for returning the hydraulic medium and a control valve associated with the control of the hydraulic energy source, the tank and the hydraulic device for the control.
- a control valve associated with the control of the hydraulic energy source, the tank and the hydraulic device for the control.
- the object is also in a transmission, in particular a dual-clutch transmission, with a gear selection and a hydraulic arrangement described above, by means of which the gear selection can be actuated solved. This results in the advantages described above.
- FIG. 1 is a schematic view of a hydraulic arrangement with a double-acting hydraulic device and a fluid path;
- Fig. 2 shows another embodiment analogous to the hydraulic arrangement shown in Figure 1 and
- Fig. 3 is a schematic view of a fluid path having a groove and a throat.
- the hydraulic device 3 has a hydraulic cylinder 9, which is acted upon by a first hydraulic access 11 and a second hydraulic access 13 opposite and double acting with a hydraulic medium. Between the hydraulic ports 11 and 13 and within the hydraulic cylinder 9, a hydraulic piston 15 is arranged, which divides the hydraulic cylinder 9 into two piston chambers 17. Each of the piston chambers 17 is assigned to one of the hydraulic inlets 11 and 13, respectively.
- the hydraulic piston 15 is a piston rod 19 assigned on both sides -in the sense of a Gleichlaufzylinders- by means of the gear selection 5 of the transmission 7 can be actuated.
- a fluid path 21 is arranged, which connects in a central position, which is shown in Figure 1, the two piston chambers 17 with each other.
- the fluid path 21 has a hydraulic resistance 23, so that air located in the piston chambers 17 can be exchanged comparatively easily and hydraulic medium located in the piston chambers 17 can be exchanged comparatively difficult between the piston chambers 17.
- the fluid path 21 ends at two hydraulic openings 25 which are assigned to the hydraulic cylinder 9.
- the hydraulic openings 25 of the hydraulic cylinder 9 are arranged at a distance from each other and arranged between the hydraulic ports 11 and 13. The distance of the hydraulic openings 25 is greater than a width of the hydraulic piston 15.
- the hydraulic inputs 11 and 13 of the hydraulic cylinder 9 are connected downstream of a control valve 29.
- the control valve 29 is designed as a spring-reset, electrically controllable proportional 4/3-way valve and is used for alternate hydraulic energizing and pressureless switching of the piston chambers 17, so that the hydraulic piston thereby shifted to the left and right.
- both hydraulic inlets 11 and 13 are assigned to a tank 31 of the hydraulic system 1 by means of the control valve 29 and thus switched without pressure.
- the hydraulic arrangement 1 has an energy source 33 connected upstream of the control valve 29.
- FIG. 2 shows a further hydraulic arrangement 1, which is constructed analogously to that shown in FIG. In this respect, reference is made to the description of Figure 1 and discussed only the differences.
- the hydraulic arrangement 1 shown in FIG. 2 has a hydraulic piston 15, to which only one side a piston rod 19 is assigned. This results in different active surfaces on the hydraulic piston 15 in the sense of a differential cylinder. Corresponding hydraulic actuating forces can be transmitted by means of the one-sided piston rod 19, this being charged accordingly to train and pressure.
- FIG. 3 shows a schematic view of an inner side of a hydraulic piston 15 of a hydraulic arrangement 1.
- a hydraulic piston 15 is shown in dashed lines.
- the inner wall of the hydraulic cylinder 9 has a groove 35 with a constriction 37.
- the groove 35 forms a fluid path 21 analogous to the fluid path 21 shown in FIGS. 1 and 2 for connecting the piston chambers 17 in the middle position of the hydraulic piston 15.
- a width of the hydraulic piston 15 is greater than a partial length of the groove 35 between a left end and the constriction 37 or between a right end and the constriction 37.
- the groove 35 may be constructed symmetrically with respect to the constriction 37.
- the fluid path 21 formed thereby is reached ineffective, so that advantageously in the end positions of the hydraulic piston 15 no unwanted leakage can take place via the fluid path 21.
- the connection by means of the fluid path 21 of the two piston chambers 17, in particular via the groove 35 or a corresponding channel, with the hydraulic resistor 33, in particular the constriction 37, can advantageously ensure a venting of the respective piston chamber 17 at a pressurization. If pressure is applied to one of the two piston chambers 17, the other is connected to the tank 31 via the control valve 29, which is designed as a 4/3-way valve.
- the channel resistance or a hydraulic resistance of the fluid path 21 can advantageously be selected so that it is very small for the air, but very large for oil or the hydraulic medium.
- the hydraulic resistance 23 may be, for example, a diaphragm or a throttle or any other hydraulic resistance.
- the fluid path 21 for example in the form of a channel, with the hydraulic resistor 23, in particular in the form of a diaphragm or a throttle, which connects the two piston chambers 17 of the double-acting hydraulic cylinder 9 of the hydraulic device 3 with each other. If the hydraulic piston 15 is in its middle position shown in FIGS. 1 to 3, wherein, for example, both piston chambers 17 can be depressurized, then the fluid path 21 connects the two piston chambers 17 to one another. In principle, it is not necessary for the hydraulic piston 15 to be located exactly in a middle position relative to the hydraulic openings 25 of the fluid path 21 in the middle position.
- both hydraulic openings 25 of the fluid path 21 are arranged so that both piston chambers 17 are connected to each other. Accordingly, an axial position can be freely selected. If the hydraulic piston 15 is in the respective end position, advantageously both hydraulic openings 25 of the fluid path 21 are within a pressure range of the respectively remaining pressurized piston space 17. Alternatively and / or additionally, it is possible that both hydraulic openings 25 are not in the pressure range, but instead only one of the hydraulic ports 25 of the fluid path 21 is in the pressure range and the other of the hydraulic ports 25 is closed by the hydraulic piston 15. For venting, a fluid path 21 is provided between the two piston chambers 17. These are connected when the hydraulic piston is in the center position.
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Chemical & Material Sciences (AREA)
- Analytical Chemistry (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
Description
Claims
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE112010003546T DE112010003546A5 (de) | 2009-09-02 | 2010-08-12 | Hydraulikanordnung mit einer doppelt wirkenden hydraulikvorrichtung |
Applications Claiming Priority (6)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102009039678 | 2009-09-02 | ||
DE102009039678.0 | 2009-09-02 | ||
DE102009039856 | 2009-09-03 | ||
DE102009039856.2 | 2009-09-03 | ||
DE102009058253 | 2009-12-14 | ||
DE102009058253.3 | 2009-12-14 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2011026458A1 true WO2011026458A1 (de) | 2011-03-10 |
Family
ID=43303876
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/DE2010/000958 WO2011026458A1 (de) | 2009-09-02 | 2010-08-12 | Hydraulikanordnung mit einer doppelt wirkenden hydraulikvorrichtung |
Country Status (2)
Country | Link |
---|---|
DE (2) | DE112010003546A5 (de) |
WO (1) | WO2011026458A1 (de) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN103790762A (zh) * | 2012-10-31 | 2014-05-14 | 财团法人工业技术研究院 | 波浪发电系统及其液压构件 |
DE102019008675A1 (de) * | 2019-12-14 | 2021-07-01 | Man Truck & Bus Se | Vorrichtung und Verfahren zum Entlüften eines Hydraulikzylinders |
Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE3935756A1 (de) * | 1989-10-27 | 1991-05-02 | Vdo Schindling | Hydraulische anlage in einem kraftfahrzeug |
FR2836704A1 (fr) * | 2002-03-01 | 2003-09-05 | Renault | Dispositif hydraulique de transmission de mouvement |
FR2843917A1 (fr) * | 2002-08-28 | 2004-03-05 | Renault Sa | Systeme hydraulique de commande d'une boite de vitesses de vehicule |
JP2007205416A (ja) * | 2006-01-31 | 2007-08-16 | Hitachi Ltd | 油圧シリンダ |
-
2010
- 2010-08-12 DE DE112010003546T patent/DE112010003546A5/de not_active Withdrawn
- 2010-08-12 WO PCT/DE2010/000958 patent/WO2011026458A1/de active Application Filing
- 2010-08-12 DE DE102010034095A patent/DE102010034095A1/de not_active Withdrawn
Patent Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE3935756A1 (de) * | 1989-10-27 | 1991-05-02 | Vdo Schindling | Hydraulische anlage in einem kraftfahrzeug |
FR2836704A1 (fr) * | 2002-03-01 | 2003-09-05 | Renault | Dispositif hydraulique de transmission de mouvement |
FR2843917A1 (fr) * | 2002-08-28 | 2004-03-05 | Renault Sa | Systeme hydraulique de commande d'une boite de vitesses de vehicule |
JP2007205416A (ja) * | 2006-01-31 | 2007-08-16 | Hitachi Ltd | 油圧シリンダ |
Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN103790762A (zh) * | 2012-10-31 | 2014-05-14 | 财团法人工业技术研究院 | 波浪发电系统及其液压构件 |
EP2728165A3 (de) * | 2012-10-31 | 2015-11-18 | Industrial Technology Research Institute | Wellenkraftwerk sowie hydraulische Komponente dafür |
US9234493B2 (en) | 2012-10-31 | 2016-01-12 | Industrial Technology Research Institute | Wave power generation system and hydraulic component thereof |
DE102019008675A1 (de) * | 2019-12-14 | 2021-07-01 | Man Truck & Bus Se | Vorrichtung und Verfahren zum Entlüften eines Hydraulikzylinders |
DE102019008675B4 (de) | 2019-12-14 | 2023-10-26 | Man Truck & Bus Se | Vorrichtung und Verfahren zum Entlüften eines Hydraulikzylinders |
Also Published As
Publication number | Publication date |
---|---|
DE102010034095A1 (de) | 2011-04-07 |
DE112010003546A5 (de) | 2012-08-23 |
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