EP0397840A1 - Hydraulische schaltungsanordnung. - Google Patents
Hydraulische schaltungsanordnung.Info
- Publication number
- EP0397840A1 EP0397840A1 EP90900115A EP90900115A EP0397840A1 EP 0397840 A1 EP0397840 A1 EP 0397840A1 EP 90900115 A EP90900115 A EP 90900115A EP 90900115 A EP90900115 A EP 90900115A EP 0397840 A1 EP0397840 A1 EP 0397840A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- hydraulic circuit
- pressure
- arrangement
- hollow
- bore
- 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
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
- 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
- F15B13/022—Flow-dividers; Priority valves
Definitions
- the invention relates to a hydraulic circuit arrangement with a pressure medium source for supplying a hydro stream, two consumers driven by partial streams of the hydro stream and a proportional flow divider valve through which the hydro stream and the two partial streams flow, the orifice arrangement of which determines the division ratio between the two partial streams ⁇ tion is provided with a first setting device for specifying the division ratio.
- the two consumers can be supplied by the hydraulic current supplied by a single pump which forms the pressure medium source. It is necessary for many applications, for example the steering of travel drives, to control the division ratio of the two partial flows supplied to the two consumers and formed by the proportional ionic flow divider valve from the hydroflow, which is done by means of the first Setting device happens. Although this allows the relative flow quantity of the two partial flows to be adjusted in relation to one another, the total flow quantity and thus also the flow quantity of the partial flows are subject to fluctuations, since the hydroflow supplied by the hydraulic pump is normally not constant. Furthermore, even with a constant total flow rate of the hydro stream, the flow rate of the two partial flows cannot be controlled.
- the invention has for its object to provide a hydraulic circuit arrangement of the type mentioned at the beginning. further develop in such a way that the flow rate can be set for two consumers fed from a single pressure medium source with partial flows of an adjustable division ratio.
- this object is achieved in that the orifice arrangement is provided with a second actuating device for specifying its total passage cross section, and the pressure medium source has a control device for load-dependent control of the hydraulic flow it supplies, at the control input of which there is a pressure difference between the pressures on both sides of the A corresponding control signal is applied to the aperture arrangement.
- Pressure medium sources whose hydroflow is regulated as a function of the load are known, for example, under the name LS pumps (load-sensing pumps).
- the control signal required to regulate the total flow rate of the hydroflow supplied by the pressure medium source is obtained in a particularly simple manner in the invention by setting the total passage cross section of the orifice arrangement to a desired predetermined value fixed with the second adjusting device.
- the pressure difference occurring with a predetermined setting of the orifice arrangement can thus be easily detected without additional circuit parts and used as the control signal required to control the control device. This means that the two consumers can be supplied with partial flows with a low structural effort, in which not only the division ratio but also the flow rate are set to the desired values.
- a configuration of the proportional flow divider valve which is particularly expedient for the hydraulic circuit arrangement consists in the fact that the orifice arrangement has an outer hollow body and an inner hollow body sealingly mounted therein, which is acted upon by the hydroflow in its interior and each has two radial flows through which the two partial flows flow Passages are provided, the axial overlap of which the overall passage cross section is determined by means of the second adjustment device by means of a mutual axial displacement of the two hollow bodies and the azimuthal overlap which determines the division ratio by means of the first adjustment device by mutual rotation of the two Hollow body is adjustable.
- the setting of the total flow rate and of the division ratio between the two partial flows is determined by the degree of overlap of the radial flow rates provided in the two hollow bodies. leave definitely.
- the radial passages are arranged relative to one another in such a way that, in the event of a mutual rotation caused by the first adjusting device, the common clear opening of the one overlapping pair of radial passages decreases as the common clear opening of the other pair of radial passages increases , whereby the division ratio of the hydro-stream passing through the radial passages into its two sub-streams is determined.
- the mutual axial displacement of the two hollow bodies by means of the second adjusting device brings about an equivalent change in the clear opening of the overlapping pairs of radial passages, so that the total flow rate is thereby set.
- a pressure compensator to be connected between the orifice arrangement and the two consumers on the control side with the pressures of the two partial flows. Since the two consumers are connected to the proportional flow divider valve via the pressure compensator, they are therefore regulated independently of the load.
- the pressure compensator has two hollow pistons which are arranged so as to be axially displaceable in a mirror-inverted manner in a bore in a housing block and which are provided with two axially spaced radial passage areas and which face one another , closed end faces, which are acted upon by the pressure of the hydraulic flow, are provided with mutually interlocking stop parts which limit their axial relative position between an extended position and a pushed-together position, and that in each case the one passage area of each hollow piston is provided with one of the partial flows of the orifice arrangement communicates and the other passage area interacts with a radial annular space of the bore of the housing block which is connected to the respective consumer and serves as a control edge.
- the housing block it finally proves to be expedient for the housing block to have a further bore radially penetrating the bore in the region between the two hollow pistons of the pressure compensator, the open end of which on one side of the bore receiving the hollow pistons of the pressure compensator has a connection for the Hydro flow forms and in which on the other side of the section bearing the hollow piston of the pressure compensator bore is arranged the diaphragm arrangement.
- FIG. 1 shows a block diagram of a hydraulic circuit arrangement
- FIG. 2 shows a sectional view of a proportional flow divider valve suitable for the circuit arrangement of FIG. 1.
- an LS pump (load-sensing pump) 1 is used to deliver a load-dependent controlled hydro stream from a hydraulic tank 2.
- the proportional flow divider valve 4 has a diaphragm arrangement 6, shown schematically in FIG. 1, on which the branching takes place between the hydroflow of the LS pump 1 occurring at a connection 7 and the two partial flows of the hydroflow occurring at connections 8, 9.
- a first actuating device 10 which can be formed, for example, by a magnetic actuator, serves to set the division ratio of the two partial flows occurring at the orifice arrangement 6 at the connections 8 and 9. Further engages the visor assembly 6, a second
- Stell ⁇ can be formed also by a magnetic membered Stell ⁇ on to the Bac properlylass- "6 cross-section of the panel assembly on a gewünsch ⁇ th predetermined value set.
- Between the An ⁇ Conclusions 8, 9 and the orifice arrangement 6 is connected to a pressure balance 12 which is acted upon on the control side by the pressures of the two partial flows occurring at the orifice arrangement 6.
- the control device of the LS pump 1 which is of a known type and therefore not shown in detail, has a control input 13 with two connections 14, 15, to which a control signal corresponding to a pressure difference is to be applied in such a way that the connection 14 in each case has the higher pressure value and the connection 15 receives the lower pressure value in each case.
- the pressure difference occurring at the orifice arrangement 6, which is via the control lines 16, 17, serves as the pressure difference 14, 15 is fed.
- the hydraulic circuit arrangement operates normally, in which the LS pump 1 supplies its hydroflow to the connection 7 of the proportional flow divider valve 4 promotes, which divides the hydraulic flow according to the setting given by the first adjusting device 10 into the two partial flows which are in a certain relationship to one another and by means of the control edges of the pressure compensator 12 feeds to the consumers 5, 5 'in a controlled manner, from where the two partial flows pass a common line 18 and the 4/3 way valve 3 flow back to the hydraulic tank 2.
- a parallel connection of two shuttle valves 19, 20 is connected between the two sides of the orifice arrangement 6.
- the change-over valve 19 is constructed in such a way that it connects the respectively higher pressure value to one connected to the control line 16 Connection 21 switches through, while the shuttle valve 20 switches the respectively lower pressure value to a connection 22 to which the control line 17 is connected. This ensures that the control signal is properly switched through to the control input of the LS pump 1 in both operating modes, namely normal operation and reversing operation.
- FIG. 2 shows an embodiment of the proportional flow divider valve 4 intended for the hydraulic circuit, in which the orifice arrangement 6 and the pressure compensator 12 are assembled in a common housing block 23.
- the housing block 23 has a bore 24 extending horizontally with its axis in the illustration in FIG. 2 and a further bore 25 crossing the bore 24 perpendicularly in the middle of its axial length.
- an outer hollow body 26 of the diaphragm arrangement 6 is axially immovable, but is rotatable about the axis in the azimuthal direction by a certain angular amount. This angular rotation of the hollow body 26 takes place in the exemplary embodiment of FIG.
- An inner hollow body 28 is sealingly mounted in the outer hollow body 26 and is supported in a rotationally fixed manner in the housing block 23 by a radial cam 30 guided in a longitudinal groove 29 of the housing block 23.
- a closing part which closes the upper end of the further bore 25 in FIG. 2 and has an axially adjustable actuator 31 serves as the second adjusting device 11.
- the outer and the inner hollow bodies 26 and 28 are each provided with two radial passages 33, 33 'and 34, 34', the mutual overlap of which is set in the axial direction by the actuator 31 and in the azimuthal direction by the screw spindle 27 .
- the clear passage opening determined by the overlap of the radial passages 33, 34 is reduced to the same extent as the clear passage opening determined by the overlap of the radial passages 33 ', 34'.
- the total passage cross section is set, the total passage cross section determined by the overlaps of the radial passages 33, 34 and 33 ', 34'.
- the hydraulic flow generated by the LS pump 1 thus flows through the open end of the further bore 25 forming the connection 7 of FIG. 1, which is opposite the closed end provided with the actuator 31, into the interior of the inner one Hollow body 28 enters and passes through the radial passages 33, 34 and 33 ', 34'.
- the partial flows of the hydraulic flow which are set with regard to the total flow quantity and the division ratio are thus available on channels 35, 35 'of the housing block 23 which communicate with the radial passages 33, 33' of the outer hollow body 26.
- each hollow piston 37, 37 ' which are oppositely opposed to one another, are arranged in an axially displaceable and sealing manner.
- Each hollow piston 37, 37 ' has two radial passage regions 38, 39 and 38', 39 ', which are axially spaced apart from one another, of which the radial passage regions 38 and 38', which are further away from the locking screws 36, 36 ', correspond to those shown in FIGS communicate the bore 24 opening channels 35 and 35 '.
- the radial passage regions 39, 39 ' which are respectively closer to the locking screws 36, 36', cooperate with radial annular spaces 40 and 40 'in the bore 24, these radial annular spaces 40, 40' via inner channels 41, 41 ' are connected to the outer connections 8 and 9 provided in the housing block 23.
- the axial position of the radial passage areas 39, 39 'with respect to the radial annular spaces 40 and 40' is selected such that the boundary edges of the annular spaces 40 and 40 'interact as control edges with the radial passage areas 39, 39', as soon as the hollow pistons 37, 37 'are displaced from their central position symmetrical to the axis of the further bore 25 under the influence of the pressure conditions.
- all radial passage areas 38, 38 ', 39, 39' are each formed by a certain number of holes which are distributed at the same angular distance around the circumference of the hollow pistons 37, 37 '.
- the hollow pistons 37, 37 ' are each provided with hook-shaped stop parts 42, 42' which, when the two hollow pistons 37, 37 'are in a maximally pulled apart position, abut one another and thereby cause a further separating movement of the Limit hollow pistons 37, 37 '.
- the stop part 42 of the hollow piston 37 is supported on the end face of the other hollow piston 37 'in a maximally pushed-together position, and returns, so that even in the maximally pushed-together position of the two hollow pistons 37, 37 'there is still a clear passage between their mutually facing end faces.
- the LS pump 1 thus conveys the hydraulic flow in the direction of arrow 43 through the channel left between the two hollow pistons 37, 37 'of the pressure compensator 12 in the further bore 25 to the interior of the inner hollow body 28 Diaphragm arrangement 6, as a result of which the two hollow pistons 37, 37 'move into their extended position.
- the partial flows of the hydroflow occurring at the orifice arrangement 6 are fed to the annular spaces 40 and 40 'via the channels 35 and 35', the radial passage areas 38 and 38 'and the radial passages 39 and 39' and through the control edges formed by these are kept constant regardless of the load and fed to the connections 8 and 9.
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Fluid-Pressure Circuits (AREA)
Description
Claims
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
CH428888A CH676347A5 (de) | 1988-11-18 | 1988-11-18 | |
CH4288/88 | 1988-11-18 | ||
PCT/EP1989/001396 WO1990005853A1 (de) | 1988-11-18 | 1989-11-18 | Hydraulische schaltungsanordnung |
Publications (2)
Publication Number | Publication Date |
---|---|
EP0397840A1 true EP0397840A1 (de) | 1990-11-22 |
EP0397840B1 EP0397840B1 (de) | 1994-06-22 |
Family
ID=4273309
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP90900115A Expired - Lifetime EP0397840B1 (de) | 1988-11-18 | 1989-11-18 | Hydraulische schaltungsanordnung |
Country Status (4)
Country | Link |
---|---|
EP (1) | EP0397840B1 (de) |
CH (1) | CH676347A5 (de) |
DE (1) | DE58907963D1 (de) |
WO (1) | WO1990005853A1 (de) |
Families Citing this family (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE19721623A1 (de) | 1997-05-23 | 1998-11-26 | Agria Werke Gmbh | Fahrzeug mit hydraulischem Einzelradantrieb |
CN101975201A (zh) * | 2010-11-02 | 2011-02-16 | 赵国普 | 单泵多执行机构液压控制系统 |
CN103671333B (zh) * | 2013-11-25 | 2016-03-30 | 湘潭市恒欣实业有限公司 | 能自动切换的双泵液压站 |
Family Cites Families (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3979908A (en) * | 1975-09-29 | 1976-09-14 | The Cessna Aircraft Company | Priority flow valve |
US4085766A (en) * | 1976-04-15 | 1978-04-25 | Bourns, Inc. | Adjustable gas mixing valve |
DE2751082C2 (de) * | 1977-11-16 | 1982-12-02 | Zahnradfabrik Friedrichshafen Ag, 7990 Friedrichshafen | Stromteilerventil für eine Hydraulikanlage |
DE2818360A1 (de) * | 1978-04-26 | 1979-11-08 | Johann Ing Grad Tyroller | Einstellbarer mengenteiler fuer fluessigkeitsstroeme bei hydraulikanlagen |
CA1192811A (en) * | 1982-08-02 | 1985-09-03 | Modular Controls Corporation | Flow divider-combiner valve |
-
1988
- 1988-11-18 CH CH428888A patent/CH676347A5/de not_active IP Right Cessation
-
1989
- 1989-11-18 DE DE58907963T patent/DE58907963D1/de not_active Expired - Fee Related
- 1989-11-18 EP EP90900115A patent/EP0397840B1/de not_active Expired - Lifetime
- 1989-11-18 WO PCT/EP1989/001396 patent/WO1990005853A1/de active IP Right Grant
Non-Patent Citations (1)
Title |
---|
See references of WO9005853A1 * |
Also Published As
Publication number | Publication date |
---|---|
DE58907963D1 (de) | 1994-08-04 |
CH676347A5 (de) | 1991-01-15 |
EP0397840B1 (de) | 1994-06-22 |
WO1990005853A1 (de) | 1990-05-31 |
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