EP2024666A1 - Hydrostatischer antrieb mit einem offenen hydraulischen kreislauf und einem geschlossenen hydraullischen kreislauf - Google Patents
Hydrostatischer antrieb mit einem offenen hydraulischen kreislauf und einem geschlossenen hydraullischen kreislaufInfo
- Publication number
- EP2024666A1 EP2024666A1 EP07725764A EP07725764A EP2024666A1 EP 2024666 A1 EP2024666 A1 EP 2024666A1 EP 07725764 A EP07725764 A EP 07725764A EP 07725764 A EP07725764 A EP 07725764A EP 2024666 A1 EP2024666 A1 EP 2024666A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- circuit
- hydraulic
- working
- hydrostatic drive
- closed
- 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.)
- Withdrawn
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
- F16H61/38—Control of exclusively fluid gearing
- F16H61/40—Control of exclusively fluid gearing hydrostatic
- F16H61/4078—Fluid exchange between hydrostatic circuits and external sources or consumers
-
- 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
- F16H61/38—Control of exclusively fluid gearing
- F16H61/40—Control of exclusively fluid gearing hydrostatic
- F16H61/4148—Open loop circuits
-
- 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
- F16H61/38—Control of exclusively fluid gearing
- F16H61/40—Control of exclusively fluid gearing hydrostatic
- F16H61/42—Control of exclusively fluid gearing hydrostatic involving adjustment of a pump or motor with adjustable output or capacity
- F16H61/421—Motor capacity control by electro-hydraulic control means, e.g. using solenoid valves
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60Y—INDEXING SCHEME RELATING TO ASPECTS CROSS-CUTTING VEHICLE TECHNOLOGY
- B60Y2200/00—Type of vehicle
- B60Y2200/40—Special vehicles
- B60Y2200/41—Construction vehicles, e.g. graders, excavators
-
- 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
- F16H61/38—Control of exclusively fluid gearing
- F16H61/40—Control of exclusively fluid gearing hydrostatic
- F16H61/42—Control of exclusively fluid gearing hydrostatic involving adjustment of a pump or motor with adjustable output or capacity
- F16H61/431—Pump capacity control by electro-hydraulic control means, e.g. using solenoid valves
-
- 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
- F16H61/38—Control of exclusively fluid gearing
- F16H61/40—Control of exclusively fluid gearing hydrostatic
- F16H61/44—Control of exclusively fluid gearing hydrostatic with more than one pump or motor in operation
- F16H61/444—Control of exclusively fluid gearing hydrostatic with more than one pump or motor in operation by changing the number of pump or motor units in operation
-
- 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
- F16H61/38—Control of exclusively fluid gearing
- F16H61/40—Control of exclusively fluid gearing hydrostatic
- F16H61/44—Control of exclusively fluid gearing hydrostatic with more than one pump or motor in operation
- F16H61/448—Control circuits for tandem pumps or motors
Definitions
- the invention relates to a hydrostatic drive with an open hydraulic circuit and a closed hydraulic circuit.
- the vehicle is the closed hydraulic circuit is not used, while in the open hydraulic circuit several hydraulic consumers can be active simultaneously. This requires a considerable dimensioning of the arranged in the open circuit hydraulic pump. This not only leads to a high investment but is also uneconomical in the operation of the vehicle.
- the invention is therefore an object of the invention to provide a hydrostatic drive with an open circuit and a closed circuit, which is improved in terms of its efficiency.
- the hydrostatic drive according to the invention comprises an open hydraulic circuit and a closed one hydraulic circuit.
- the closed hydraulic circuit has at least one working circuit and one driving circuit.
- the open hydraulic circuit is connected to at least one hydraulic consumer of a working hydraulics. In this way, when the vehicle is at a standstill, the working hydraulics comprising a plurality of hydraulic consumers are connected for actuation both to an open circuit hydraulic pump and to a closed loop hydraulic pump.
- the working hydraulics has individual hydraulic consumers. There is an allocation of a part of these hydraulic consumers to the hydraulic pump of the open circuit. In contrast, at least one further hydraulic consumer of the working hydraulics is connected to the closed circuit in a working cycle. This is particularly advantageous because usually both the open circuit and the closed circuit are driven by a common drive machine. In this case, both hydraulic pumps are usually connected to the prime mover at the same time. Upon actuation of the working hydraulics, therefore, the hydraulic pump of the drive hydraulics is also driven anyway.
- the inventive division of the hydraulic load of the working hydraulics on the open circuit and the closed circuit the losses are minimized and at the same time it is possible to make the pump in the hydraulic circuit in terms of their performance smaller. The weight savings achieved thereby leads, in addition to a reduction in the original investment, to a reduction in fuel consumption during driving, since the total mass of the vehicle is reduced.
- valve device in the closed hydraulic circuit, by means of which it is possible to switch between the working cycle and the travel cycle.
- valve device thus in each case a closed hydraulic partial circuit is formed, in which the hydraulic pump is arranged.
- the currently not required second circuit part is decoupled. Uncoupling the drive circuit thus ensures that accidental driving of the drive wheels is prevented.
- the working cycle can contain allocation valves with which several consumer line branches can be assigned to the respective suction or pressure-side working lines of the closed circuit.
- the valve block may also have a load-holding valve and / or a pressure-limiting valve. Since the valve block is assigned to the working cycle, regardless of possibly already existing pressure limiting valves to secure the closed circuit, a hedge of the working cycle and in particular of the hydraulic consumer itself can be done.
- a purge valve is additionally provided in the valve block.
- the hydraulic pumps of the open circuit and the closed circuit are mechanically interconnected according to a further preferred embodiment, so that a rigid coupling between the two pumps is possible.
- This has the particular advantage that at a most oppressive load in the further hydraulic consumer a
- the hydraulic pump of the closed circuit is adjustable in its delivery volume and designed to convey pressure medium in two directions.
- the control of the further hydraulic consumer takes place by adjusting the conveying direction and the required flow rate.
- Complex control via reducing valves and adjustable throttles can thus be dispensed with.
- the combination with a lifting cylinder is provided as a further hydraulic consumer.
- Fig. 1 is a schematic representation of the hydrostatic drive according to the invention.
- the hydrostatic drive 1 comprises an open circuit 2 and a closed circuit 3.
- a hydraulic pump unit 4 is provided which has an adjustable hydraulic pump 5.
- the adjustable hydraulic pump 5 is coupled to a feed pump 6 to the hydraulic pump unit 4.
- the hydraulic pump 5 is provided for generating a delivery flow in the closed hydraulic circuit 3 and connected to a first working line 7 and a second working line 8.
- the hydraulic pump 5 is designed for conveying in both directions.
- Circuit 3 comprises in addition to the hydraulic pump 5, the first working line 7 'and the second working line 8', a hydraulic motor 9.
- the hydraulic motor 9 is adjustable in the illustrated embodiment in its displacement and a first working line section 7 'and a second working line section 8' with the first Working line 7 and the second working line 8 and thus connected to the hydraulic pump 5.
- the hydraulic motor 9 is connected via an output shaft 10 with a differential gear 11.
- the differential gear 11 is, for example, a rear axle of a mobile machine.
- the torque applied to the differential gear 11 acts on a first half-wave 12 and a second half-wave 13 on a first and a second drive wheel 14, 15th
- connection of the hydraulic motor 9 with the hydraulic pump 5 takes place via a first
- a further hydraulic pump 17 is provided, which is arranged in the open circuit 2.
- the further hydraulic pump 17 is also in her Volume adjustable, but only designed for conveying in one direction.
- a working hydraulic 18 is actuated by the entire hydrostatic drive 1.
- the working hydraulics; 18 includes in the illustrated embodiment, a first hydraulic cylinder 20, a second hydraulic cylinder 21 and a third hydraulic cylinder 23.
- the first and second hydraulic cylinders 20, 21 are acted upon by the further hydraulic pump 17 of the open hydraulic circuit 2 with pressure medium.
- the third hydraulic cylinder 23 is, however, associated with the closed hydraulic circuit 3 and is coupled to the hydraulic pump 5 via the valve block 16, provided that the closed hydraulic circuit 3 is not required for the traction drive.
- the first hydraulic cylinder 20 is designed in the illustrated embodiment as a double-acting lifting cylinder, wherein in the first hydraulic cylinder 20, a piston 24 is arranged, which divides the first hydraulic cylinder 20 into a piston surface space 27 and a piston rod space 28.
- a second piston 25 is provided in the second hydraulic cylinder 21, which in turn subdivides the second hydraulic cylinder 21 into a piston surface space 29 and a piston rod space 30.
- the closed hydraulic circuit 3 associated third hydraulic cylinder 23 has in a corresponding manner to a piston 26 which is arranged longitudinally displaceable in the third hydraulic cylinder 23.
- the hydraulic cylinder 23 is also divided into a piston surface space 31 and a piston rod chamber 32.
- the pistons 24, 25 and 26 are respectively on the side of the
- Piston surface space 27, 29 and 31 and on the oriented in the opposite direction surface in the piston rod chamber 28, 30, 32 acted upon by a control pressure.
- the signal pressure for the first Working cylinder 20 and the second working cylinder 21 through the open hydraulic circuit 2 and the arranged therein further hydraulic pump 17 is generated.
- pressure is generated by the hydraulic pump 5. Because of the
- the closed hydraulic circuit 3 is formed alternately by a drive circuit 36 or a working circuit 37.
- the components of the circulation circuit 36 have already been discussed, which comprises the first working line branch 7 ', the hydraulic pump 9 and the second working line branch 8'.
- the circulation circuit 36 together with the first working line 7 and the second working line 8 and the hydraulic motor 5, the closed hydraulic circuit 3 when a driving operation is required.
- the working cycle 37 comprises in addition to the third
- Hydraulic cylinder 23 a first consumer line 38 and a second consumer line 39, which are connected via the valve means of the valve block 16 with the first working line 7 and the second working line 8. If the vehicle is stationary, it is possible to switch between the working circuit 37 and the travel circuit 36.
- a first switching valve 40 and a second switching valve 41 which form the valve device, are preferably arranged in the valve block 16 for this purpose.
- Switching valve 41 are connected to each other via a coupling rod 42, so that a common operation is possible.
- the first switching valve 40 and the second switching valve 41st the first working line 7 is connected to the first working line section 7 '.
- the second working line 8 is connected to the second working line section 8 '.
- an electromagnetic actuation is provided on the first switching valve 40.
- the first switching valve 40 is acted upon by an electromagnet 43 in the direction of its second switching position. The movement that the
- Solenoid 40 generated in the first switching valve 40 is transmitted via the coupling rod 42 to the second switching valve 42, which is consequently also moved to its second switching position.
- the movement on the first switching valve 40 and the second switching valve 41 is performed against a compression spring 44 provided on the second switching valve 42. If the electromagnet 43 is no longer energized, so the second switching valve 41 and consequently the first switching valve 40 is again in its first by the compression spring 44
- the first switching valve 40 and the second switching valve 41 are provided in the illustrated embodiment alone to between the travel circuit 36 and the
- the activation of the electromagnet 43 can therefore be advantageously coupled to an idling sensor, for example.
- the allocation valve block 48 connects to the assignment of the piston rod chamber 32 and the piston surface space 31 to the first working line 7 or to the second working line 8 either a first Bistechnischszweig 38 'with the first consumer line 38 and at the same time a second Cir effetszweig 39' with the second consumer line 39 or the first Self effetszweig 38 'with the second consumer line 39 and the second consumer line branch 39 'with the first consumer line 38.
- the assignment valve block 28 can preferably also be realized with simple switching valves.
- the positioning speed and adjusting direction is determined by adjusting the variable hydraulic pump 5.
- the open hydraulic circuit 2 comprises, in addition to the further hydraulic pump 17, a suction line 49.
- the further hydraulic pump 17 sucks in pressure medium via the suction line 49 from a tank volume 50 and delivers it to a delivery line 51.
- the delivery line 51 can be connected by a first control valve unit 52 to a first connection line 54 or a second connection line 55.
- a supply of pressure medium from the delivery line 51 into the piston surface space 29 or the piston rod space 30 of the second hydraulic cylinder 21 is possible via a third connecting line 56 or a fourth connecting line 57.
- connection of the third connection line 56 and the fourth connection line 57 to the delivery line 51 via a second valve unit 53 The first valve unit 52 and the second valve unit 53 are preferably integrated in a common housing. Instead of a connection of the delivery line 51 with one of the connecting lines 54 to 57, a connection to an expansion line 57 can be produced by the valve units 52, 53. If, for example, a stroke movement of the piston 24 of the first hydraulic cylinder 20 is to be performed by pressing the piston surface space 27, the first connection unit 54 connects the first connection unit 54 to the delivery line 51. At the same time, in order to enable a volume compensation, the second connecting line 55 of the piston rod chamber 28 is connected to the expansion line 57. The displaced from the piston rod chamber 28 pressure fluid is thus discharged into the tank volume 50.
- the actuation of the second hydraulic cylinder 21 takes place in the same way, so that it can be dispensed with a new description.
- the first valve unit 52 and the second valve unit 53 can be actuated together or separately from one another and are connected to the delivery line 51 and the expansion line 57 via common connections.
- a common drive motor 45 which is coupled via a drive shaft 46 with the hydraulic pumps 5, 6, 17.
- a feed pump 6 is provided in the hydraulic pump unit 4 in addition to the hydraulic pump 5.
- the feed pump 6 sucks on a feed pump suction 58 also from the tank volume 50 pressure medium and promotes it via a
- Supply pressure line 59 in a not shown feed pressure system.
- any other hydraulic consumer can be used.
- the individual hydraulic consumers of the working hydraulics 18 do not have to have the same embodiment.
- a hydraulic cylinder which usually is only pressurized to provide 3 in the closed hydraulic circuit.
- the weight which presses on the piston rod 35 generates in the piston surface space 31 a pressure which is supplied via the second consumer line branch 39 'and the valve block 16 of the hydraulic pump 5 and is supported there.
- the hydraulic pump 5 acts as a hydraulic motor and generates a torque which is supplied via the drive shaft 46 of the further hydraulic pump 17.
- the common drive machine 45 thus only needs to generate a reduced torque for driving the further hydraulic pump 17, whereby the fuel consumption of the drive motor 45 decreases.
- a load-holding valve is preferably arranged in the allocation valve block 48, which connects between the first and second consumer line branch 38 ', 39' and the first consumer line 38 and the second consumer line 39 interrupts.
- a flushing valve can preferably also be integrated in the common valve block 16, which in particular contains all the valves required for operating the circulation circuit 36 and the working cycle 37.
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE200610025985 DE102006025985A1 (de) | 2006-06-02 | 2006-06-02 | Hydrostatischer Antrieb mit einem offenen hydraulischen Kreislauf und einem geschlossenen hydraulischen Kreislauf |
PCT/EP2007/004884 WO2007140945A1 (de) | 2006-06-02 | 2007-06-01 | Hydrostatischer antrieb mit einem offenen hydraulischen kreislauf und einem geschlossenen hydraullischen kreislauf |
Publications (1)
Publication Number | Publication Date |
---|---|
EP2024666A1 true EP2024666A1 (de) | 2009-02-18 |
Family
ID=38370390
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP07725764A Withdrawn EP2024666A1 (de) | 2006-06-02 | 2007-06-01 | Hydrostatischer antrieb mit einem offenen hydraulischen kreislauf und einem geschlossenen hydraullischen kreislauf |
Country Status (4)
Country | Link |
---|---|
EP (1) | EP2024666A1 (de) |
CA (1) | CA2625203A1 (de) |
DE (1) | DE102006025985A1 (de) |
WO (1) | WO2007140945A1 (de) |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102015121782A1 (de) * | 2015-12-15 | 2017-06-22 | Linde Hydraulics Gmbh & Co. Kg | Mobile Arbeitsmaschine mit einem hydrostatischen Fahrantrieb und einer Arbeitshydraulikpumpe |
Family Cites Families (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE3462861D1 (en) * | 1983-09-15 | 1987-05-07 | Zahnradfabrik Friedrichshafen | Hydrostatic-mechanical transmission arrangement |
US4754603A (en) * | 1987-07-20 | 1988-07-05 | Rosman Allan H | Hydraulic-drive system for an intermittent-demand load |
DE19751001A1 (de) * | 1997-11-18 | 1999-05-20 | Zahnradfabrik Friedrichshafen | Verfahren und Vorrichtung zur Verhinderung der Zugkraftunterbrechung beim Zu- und Abschalten von Hydromotoren |
US6601474B2 (en) * | 2000-09-05 | 2003-08-05 | Kanzaki Kokyukoki Mfg. Co., Ltd. | Hydrostatic transmission and power train for vehicle |
DE102004044510A1 (de) * | 2004-09-15 | 2006-03-30 | Zf Friedrichshafen Ag | Hydraulisches Getriebe |
-
2006
- 2006-06-02 DE DE200610025985 patent/DE102006025985A1/de not_active Withdrawn
-
2007
- 2007-06-01 EP EP07725764A patent/EP2024666A1/de not_active Withdrawn
- 2007-06-01 WO PCT/EP2007/004884 patent/WO2007140945A1/de active Application Filing
- 2007-06-01 CA CA002625203A patent/CA2625203A1/en not_active Abandoned
Non-Patent Citations (1)
Title |
---|
See references of WO2007140945A1 * |
Also Published As
Publication number | Publication date |
---|---|
WO2007140945A1 (de) | 2007-12-13 |
DE102006025985A1 (de) | 2007-12-06 |
CA2625203A1 (en) | 2007-12-13 |
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