EP1497559B1 - Hydraulische steueranordnung in load-sensing technik - Google Patents
Hydraulische steueranordnung in load-sensing technik Download PDFInfo
- Publication number
- EP1497559B1 EP1497559B1 EP03724956A EP03724956A EP1497559B1 EP 1497559 B1 EP1497559 B1 EP 1497559B1 EP 03724956 A EP03724956 A EP 03724956A EP 03724956 A EP03724956 A EP 03724956A EP 1497559 B1 EP1497559 B1 EP 1497559B1
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- EP
- European Patent Office
- Prior art keywords
- valve
- pressure
- control
- line
- spring
- 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.)
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Classifications
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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
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
- F15B11/161—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load
- F15B11/165—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load for adjusting the pump output or bypass in response to demand
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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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
- F15B2211/205—Systems with pumps
- F15B2211/2053—Type of pump
- F15B2211/20538—Type of pump constant capacity
-
- 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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/50—Pressure control
- F15B2211/505—Pressure control characterised by the type of pressure control means
- F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
- F15B2211/50536—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using unloading valves controlling the supply pressure by diverting fluid to the return line
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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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/50—Pressure control
- F15B2211/51—Pressure control characterised by the positions of the valve element
- F15B2211/513—Pressure control characterised by the positions of the valve element the positions being continuously variable, e.g. as realised by proportional valves
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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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/50—Pressure control
- F15B2211/515—Pressure control characterised by the connections of the pressure control means in the circuit
- F15B2211/5157—Pressure control characterised by the connections of the pressure control means in the circuit being connected to a pressure source and a return line
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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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/50—Pressure control
- F15B2211/52—Pressure control characterised by the type of actuation
- F15B2211/528—Pressure control characterised by the type of actuation actuated by fluid pressure
-
- 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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/50—Pressure control
- F15B2211/56—Control of an upstream pressure
-
- 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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/60—Circuit components or control therefor
- F15B2211/605—Load sensing circuits
- F15B2211/6051—Load sensing circuits having valve means between output member and the load sensing circuit
- F15B2211/6054—Load sensing circuits having valve means between output member and the load sensing circuit using shuttle valves
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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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/60—Circuit components or control therefor
- F15B2211/605—Load sensing circuits
- F15B2211/6051—Load sensing circuits having valve means between output member and the load sensing circuit
- F15B2211/6055—Load sensing circuits having valve means between output member and the load sensing circuit using pressure relief valves
-
- 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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/60—Circuit components or control therefor
- F15B2211/65—Methods of control of the load sensing pressure
- F15B2211/654—Methods of control of the load sensing pressure the load sensing pressure being lower than the load pressure
Definitions
- a first directional control valve can be supplied via the pressure medium to a first hydraulic consumer, and at least one further directional control valve, via the pressure medium to another hydraulic Consumable can be supplied and preferably with the first directional control valve is summarized to a valve block, and a load-sensing control having.
- a hydraulic control arrangement is e.g. known from DE 197 15 021 A1. It is a hydraulic one Control arrangement according to the load-sensing principle, at a variable displacement pump or a constant pressure pump associated bypass pressure balance depending on one with the highest load pressure of the actuated hydraulic consumer changing control pressure, preferably in dependence from the load pressure itself, each set so that the pump pressure by a certain pressure difference, the control ⁇ p, above the highest load pressure lies.
- the control pressure is a load-sensing control valve, which by a Control valve of the variable displacement pump or is realized by the bypass pressure compensator, fed via a load signaling line. This is made up of one of the number of Directional valves corresponding number of line sections together. each Directional control valve has an individual signaling channel. Shuttle valves serve to the highest pressure leading individual signaling channel with the load reporting line and their line sections to connect with each other.
- the pressure medium flows through adjustable, usually Metering orifices formed on the spools of the directional control valves to, between an outgoing from the variable delivery pipe and the hydraulic consumers are arranged. Because of the highest Load pressure independent pressure difference between the highest load pressure and the pump pressure depends on the speed at which the highest pressure pressure hydraulic, consumer moves, solely from the flow area of the corresponding Metering off.
- the pump, inlet or system pressure in a load-sensing hydraulic control arrangement thereby to a Limit pressure are limited, that in the connected to the control valve, first line section of the load-sensing line provides a nozzle and between this and the control valve to the first line section a pressure relief valve followed.
- the pump pressure will not increase by more than that Control ⁇ p above the limit pressure set with the pressure relief valve.
- the load pressure with which a hydraulic consumer maximum can be applied individually adjusted. This is according to DE 197 15 021 to the individual reporting channel of the corresponding directional valve section downstream of a nozzle, a pressure relief valve connected. This limits the control pressure in the spring chamber of the individual pressure compensator.
- the pressure balance closes when the pressure upstream of the orifice greater than the control pressure increased by the control ⁇ p of the individual pressure compensator.
- the load pressure can therefore only rise to a pressure which is around the Control ⁇ p of the individual pressure compensator above the set pressure of the pressure relief valve lies. However, this is in the directional valve section of the hydraulic Consumer an individual pressure balance necessary.
- the invention is based on the object, a hydraulic control arrangement, having the features of the preamble of claim 1, so to further develop, that the load pressure for a hydraulic consumer to cost Way to a lower value than for another hydraulic one Consumer is limited, regardless of the lower value is limited, whether the second function alone or together with the first function is pressed. This is intended to safely protect the second function from excessive pressure become.
- the desired goal is inventively achieved in that in the hydraulic Control arrangement with the features of the preamble of the claim 1 the Vor Kunststoffventitan extract at a certain, in another Line section of the load-sensing line pending pressure from a high, first Limit pressure to a lower, second limit pressure is adjustable and that the individual message channels, from the first line section of the load reporting line from the perspective of decreasing maximum load pressure of hydraulic consumers connectable to the successive line sections of the load signaling line are.
- a control arrangement according to the invention serves to actuate two or more groups of one or more hydraulic consumers, where the groups differ in maximum Different load pressures.
- the directional valve sections after falling maximum load pressure orderly. Is a hydraulic consumer from a group that does not have the has the highest maximum load pressure actuated, so is via the associated shuttle valve the corresponding line section of the load reporting line with the Load pressure applied. With this pressure, the pilot valve arrangement is so controlled, that the pressure in the first line section of the load signaling line between the nozzle and the control valve a lower maximum load pressure at least then do not exceed the corresponding maximum control pressure can if the lower maximum load pressure at the corresponding consumer is reached.
- the pilot valve assembly according to claim 3 a between the first line section and a discharge line arranged pilot valve, whose set pressure For example, between two pressure levels is changeable.
- the pilot valve can be a pressure relief valve with two pressure levels be and be with a valve element that of the directly at the valve inlet applied pressure in the opening direction is applied. It is, too possible that the valve element one between the first line section of the Lastmeldetechnisch and a discharge line arranged or in between switchable pilot valve in the opening direction of the pressure on the control valve the remote side of the nozzle is applied.
- the pilot valve is then the control pressure in the line section between the nozzle and the control valve, to it with its main entrance separated from a control entrance is connected to one of the control ⁇ p below the set pressure limit lying pressure.
- a first possibility to obtain two pressure stages of the pilot valve is, as stated in claim 4, therein, the bias of a Valve spring to change the movable valve element of the pilot valve against a pressure force generated on an active surface of the valve element in the direction a closed position acted upon.
- an auxiliary piston is used to over the the biasing force of the valve spring between two by a first fixed stop and a second fixed stop defined values is changeable.
- the auxiliary piston has an effective area which is larger than the effective area on Valve element, so that upon application of the two active surfaces on the valve element and at the auxiliary piston with the same pressure of the auxiliary piston, the valve spring first biasing more, before with further increasing pressure the pilot valve opens, and then its by the higher value of the spring preload defining stop certain situation safely maintains.
- Switching position of a changeover valve is the effective area on the auxiliary piston relieved of pressure or acted upon by pressure.
- the two stops independently adjustable by turning two setscrews are.
- structurally advantageous embodiments of the hydraulic Control arrangement according to claim 5 or 6 can be found in the Claims 7 to 9 is particularly preferred, inter alia, that the valve spring at the valve element remote end of the auxiliary piston is supportable, so this end of the auxiliary piston is displaceable. This appears structurally simpler than a principle also possible change of the spring preload by a displacement of a valve seat for the valve element.
- the response pressure of a valve, on the valve element in the opening direction or more generally, in one direction a compressive force and in the opposite Direction a spring force acts, can not be changed only by a change the spring bias, but also by a change in the effective Change effective area for the upcoming pressure.
- valve element by a in the first line section of Lastmeideleitüng and at a first control surface applied pressure in the opening direction acted upon is and that a second control surface is present on an auxiliary piston, the on the valve element acts and as a function of the pressure in the another line section of the load-sensing line certain switching position of a Reversing valve of pressure relieved or pressurizable.
- the valve element by a on the second control surface applied pressure in the closed position, wherein the second control surface is smaller than the first control surface.
- the switching valve can be a simple and inexpensive 2/2 way valve with a single control edge, if it according to claim 13 in series with a nozzle between the load-sensing line and a discharge line arranged is, with the control chamber on the auxiliary piston at the connection between the nozzle and 2/2 way valve is located.
- the switching valve can according to claim 14 also be a 3/2 way valve, which has a control chamber on the auxiliary piston in one Seed position with the load indicator line and in the other switching position with connects a discharge line.
- Direct-operated valves that operate in stages at different set pressures are adjustable, are rarely needed, are special constrictions and are therefore relatively expensive to manufacture.
- Made in mass production Valves may be used for the pilot valve assembly, if these according to claim 15, a first, between the first line section and a relief line arranged or switchable between pilot valve and a second, between the load-sensing line and the discharge line arranged or interposed switchable pilot valve and the set pressure of the second pilot valve is less than the set pressure of the first Pilot valve is.
- the following is achieved.
- the entrance of the second as. Pressure relief valve trained pilot valve downstream of a nozzle with a first further line section of Lastmeldeteitung or connected to the associated individual Lastmeldekanal is, in the solo mode of the associated function (directional valve section) is the system pressure limited by the response pressure of the second pilot valve.
- this function with a further forward and on a higher pressure safe function (directional valve section) against it The pump pressure may rise to the higher value because of the LS branch the front function reported a higher control pressure to the control valve can be.
- the switching valve Upon actuation of the function (directional valve section), the one first further line section assigned to the rear following line section is, the switching valve is switched and thereby the pressure in the first Line section of the load signaling line to the low set pressure of the limited second pilot valve, so that the system pressure on the low Value is limited.
- the system pressure at a Parallel operation of several hydraulic consumers over the by the set pressure of the second pilot valve. conditional value increase, as long as the Load pressure of the lower pressure protected hydraulic consumer is below the set pressure of the second pilot valve. Only when the load pressure on the response pressure of the second pilot valve increases limited this the control pressure on the control valve to one by the control ⁇ p below the set pressure value.
- the claims 19 to 21 relate to the advantageous housing the pilot valve assembly in a directional control valve section with single-acting Function in which the free space of unnecessary consumer connection is available.
- the switching valve is advantageously perpendicular to the Plane of the directional valve disc arranged as the perpendicular to the disc planes extending control line for the pressure signal for adjusting the pilot valve assembly directly on the flange surface of the single-acting directional valve section can open into the switching valve.
- a control block 15 which is for a forklift is provided, four-way valve disks 16, 17, 18 and 19, an input disk 20 having an inlet port 21 and a drain port 22, and an end plate 23, with the one from the inlet port 21 through the input disk and the directional valve discs through inlet passage 24 closed is.
- From the drain port 22 goes through the input disk and the directional valve discs through a drain channel 25 which leads into the end plate.
- From the drain port 22 hydraulic oil can flow to a tank 26.
- the inlet connection is connected to the pressure connection of a hydraulic pump 27, thus promote the sucked from the tank hydraulic oil into the inlet channel 24 can.
- the directional valve disk According to their order from the input disk 20, let the directional valve disk be 16 the first or foremost, the directional control valve disc 17 the second, the Directional valve disc 18, the third and the way valve disc 19, the last or rearmost. If in the following components or channels within a directional valve disc be named as first, second, third or last, this should be clearly on their Indicate affiliation to the appropriate directional valve disc.
- Each directional valve disc includes a proportionally adjustable directional control valve 28, 29, 30 and 31, with a hydraulic consumer, in a forklift Hydraulic cylinder, controlled according to the amount and direction of the speed can.
- the directional valve 28 of the first directional valve disc 16 is the function "lifting" associated with the fork, for a single-acting hydraulic cylinder is sufficient.
- the directional valve 29 of the second-way valve disc 17 is the function “tilt" the mast and the directional valves 30 and 31 of the directional control valves 18 and 19 are additional functions such as “extension of the fork" and “sideways movement of the Fork "for these functions are the hydraulic consumers double-acting hydraulic cylinders.
- a shuttle valve is located in each directional control valve disc 35, 36, 37 and 38 with a valve body 39.
- a shuttle valve connects one from the center port of the shuttle valve starting LS-Kanat 40, 41, 42 and 43 a directional valve disc with an individual Signal box 44, 45, 46 and 47 a directional control valve disc or with the LS channel of the following directional control valve disc.
- the one side port of the shuttle valve 38 of the last directional valve disc is on the end plate 23 with the Drain channel 25 connected.
- each directional valve disc in turn, via the associated directional control valve in a working position of Directional valve connected to the flow to the hydraulic consumer, so that in it the load pressure of the hydraulic consumer is present, and in the neutral position of the directional control valve to the drain line relieved of pressure.
- a nozzle 50 is inserted in the first LS channel 40.
- the hydraulic pump 27 is a constant displacement pump.
- the load-sensing controller will formed by a pressure compensator 51, which housed in the input disk 20 is and between the inlet channel 24 and the drain channel 25 is located.
- a control piston the pressure compensator is in the opening direction of the pump pressure in the inlet channel 24 charged.
- a compression spring 52 and a control pressure in the LS channel 40 on of the shuttle valve 35 remote side downstream of the nozzle 50 is present.
- the Both surfaces on which the control pressure and the pump pressure act are same size.
- the control piston is free of force when the pump pressure around the Pressure equivalent of the compression spring 52 is higher than the control pressure.
- This pressure difference is also referred to as a rule ⁇ p and usually has a value between 5 bar and 20 bar.
- the hydraulic pump 27 is a variable displacement pump with a schematically indicated load-sensing control valve 53 whose Regulating piston in the sense of an adjustment of the hydraulic pump in the direction of larger Stroke volume of the control pressure downstream of the nozzle 50 and a control spring and is acted upon by the pump pressure in the direction of smaller displacement.
- a pump pressure is adjusted, which is the pressure equivalent of the Control spring corresponding control ⁇ p above the control pressure downstream of the nozzle 50th lies.
- the use of a load-sensing regulated variable pump brings less Loss of unusable energy with it, because not only the pump pressure, but also the pump delivery is limited to the necessary level.
- the LS channel 40 is in the input disk 20 continued and via a LS connection 54 and a line with the on the Hydraulic pump 27 constructed control valve 53 connected.
- a directly controlled pressure relief valve 55 whose entrance to the downstream of the nozzle 50 lying part of the LS channel 40 and whose output is connected to the drain channel 25.
- Directly controlled pressure relief valve means that from the figures 2 and 3 apparent movable valve element 56 in the opening direction of an effective Effective area of the pressure at the entrance of the valve and in the closing direction of a Valve spring 57 is acted upon.
- the pressure relief valve 55 leaves the Pressure at its entrance only to a limit pressure rise, which at the Active surface generates a compressive force that is equal to the spring force.
- valve spring 57 the spring force between two determined by two stops for one end of the valve spring 57 Values changeable.
- the valve element 56 remote end of Valve spring 57 can do this by an auxiliary piston 58 in the direction of a valve seat be moved on the in the closed state of the valve 55 the Valve element 56 is seated.
- the auxiliary piston adjoins with an effective surface to one Control chamber 59, the pressurization of the switching position of a switchable between two switching positions and also in the directional control valve disc 16 built-way valve depends.
- a directional control valve 60 with two terminals, so a 2/2 way valve, which is in series with a nozzle 61 and downstream of this the LS channel 40 upstream of the nozzle 50 and the drain channel 25 is arranged.
- the auxiliary piston 58 with the in the LS channel upstream of the nozzle 50 applied pressure and spans the Valve spring strong before, so that the limit pressure is high. If the directional valve is open, so the auxiliary piston is relieved of pressure. The valve spring 57 is less biased and the limit pressure is lower
- a valve piston 62 of the directional control valve 60 is in the closing direction of a compression spring 63 loaded and in the opening direction via a through the directional control valve plate 17th passing control line 64 from that in the third LS channel 42 pending Pressure acted upon.
- the force of the compression spring 63 can be selected be that the directional valve already at a very low pressure of, for example 10 bar opens.
- the compression spring can also be set to a higher pressure be, but in any case is so low that when operated directional control valve 30 the pressure limiting valve 55 is set to the low limit pressure, before the higher limit pressure is reached.
- the third LS channel 42 is in the third position Pressure on.
- Switches the directional control valve 60 for example, already at 10 bar pressure in the Control line 64 um, then, as soon as this load pressure on one of the directional control valves 30 and 31 controlled consumer occurs, the pressure relief valve adjusted to the low limit pressure of 60 bar.
- the pump pressure can then to a maximum of 70 bar.
- the load pressure can be higher on the third or fourth Consumers will not. Will be the first or second consumer at the same time controlled, this only moves when its load pressure is lower than 70 bar is.
- the load pressure at the third or fourth consumer is then also at 70 bar limited when the directional control valve 60 switches only at 70 bar.
- the pump pressure is then via the Zumeßblende in the directional control valve 30 or 31 to the load pressure of the third or fourth hydraulic consumer throttled. If this consumer finally reaches an attack, it rises its load pressure to 70 bar, so that the directional control valve 60 switches and the Pressure relief valve 55 adjusted to the low limit pressure of 60 bar becomes.
- the pump pressure goes back to 70 bar; so that even with open directional valve 30 or 31 and without oil flow the load pressure at the third or fourth hydraulic Consumer remains limited to 70 bar.
- the valve body 39 of the shuttle valve 35 is in a Recess 70 in the voltage applied to the directional control valve disc 17 flange surface the directional valve disk 16.
- the valve body 39 takes a such a situation that the LS channel 41 or the message channel 44 with the LS channel 40 is connected.
- the two valves 55 and 60 are in the directional control valve disc 16 perpendicular to the plane the directional valve disc 16 of the voltage applied to the directional control valve disk 17 Flange surface installed.
- the compression spring 63 is clamped. These seeks to hold the valve piston in contact with the directional valve disc 17.
- the Blind bore 65 opens a transverse channel 71, the upstream of the nozzle 50 of the LS channel 40 goes out and in which the nozzle 61 is located.
- the Blind bore 65 cut by a channel 72, which is connected to the drain channel 25th connected is. Also, the space in which the compression spring 63 is located, depressurized. Axial opens into the blind bore 65 in the directional control valve 17th extending control channel 64.
- the valve piston 62 takes under the influence of the compression spring 63 a rest position a, in which he is pressed to the directional valve disc 17. In this rest position the two channels 71 and 72 are sealed against each other. Exceeds the by the pressure in the control channel 64 at the cross-sectional area of the valve piston 62 generated compressive force the spring force, the valve piston is to the stop moved to the bottom of the blind bore 65 in its second switching position, in the downstream of the nozzle 61 lying part of the channel 71 with the channel 72nd connected and thus relieved of pressure.
- the individual parts of the pressure limiting valve 55 are in a blind bore 73, in the center at the bottom of a downstream of the nozzle 50 with the LS channel 40th connected channel 74 opens The mouth edge of the channel 74 forms a seat for the formed as a ball valve element 56 of the pressure relief valve.
- the Ball is held in a spring plate 75 for the valve spring 57, which extends over a another spring plate 76 at one to a stop in the blind hole 73 screwed screw 77 can support.
- the distance of two spring plate from each other when supporting the one on the ball 56 on Seat and the other on the screw determines a low bias the valve spring 57. By washers between the screw 77 and the spring plate 76, this bias can be adjusted.
- the guide cross section, with the auxiliary piston 58 is guided in the screw 77 and the equal to the effective area for the pending in the control chamber 59 and the auxiliary piston is to be applied in the direction of the valve element 56 pressure is greater than the seat cross-section for the valve element 56, so that when closing the Wegeventüs 60 of the auxiliary piston 58, first the valve spring 57 to the abutment of the stop collar 78 on the screw 77 will bias more, before continuing on rising pressure in the LS channel 40, the pressure relief valve opens. The higher one Preload the valve spring 57 can by washers on the stop collar 78 to be adjusted.
- the directional control valve 60 is the same as formed in Figure 2 and as well as there perpendicular to the plane of the disc
- Directional valve disc 16 arranged in this in a blind bore 65.
- the items the pressure relief valve 55, however, are in a blind hole 73, whose axis is parallel to the disc plane and perpendicular ( Figure 3) or parallel extends to the axis of the valve bore, of which the spool 10 of the directional control valve 28 is recorded.
- this Disk is provided for the actuation of a single-acting hydraulic cylinder and therefore has only one consumer outlet, especially a lot of room for the Housing the valves 55 and 60 available.
- the pressure relief valve of Figure 3 which is parallel to the one consumer terminal protrudes from the directional control valve disc, has a screwed Valve seat 80 for the again designed as a ball valve element 56.
- the Valve spring 57 is supported on the spring plate 75 on the ball 56 from.
- Above the Spring plate 76 is able to support the valve spring 57 on the screw insert 77, which is now provided with a radial seal and to adjust the low Pretension of the valve spring can be rotated.
- the twist is, however only possible if another provided with a radial seal Screw insert 81 is not located in the bore 73.
- the auxiliary piston 58 mounted with its stop collar 78.
- the screw 81 can with a Lock nut secured and sealed with a protective cap.
- FIG. 6 and 7 uses like that after Figure 1, the 2/2 way valve 60 and the nozzle 61 to the adjustment of a pressure relief valve 55, with its entrance in turn downstream of the Nozzle 50 to the LS channel 40 and connected with its output to the drain channel 25 is.
- the mouth rim the channel 74 in turn forms the seat for the valve element designed as a ball 56.
- the ball is held in the spring plate 75 for the valve spring 57, the Furthermore, now directly on the screwed into the blind hole 73 Screw insert 77 is supported.
- the screw 77 is with a radial seal provided, with the aid of the control chamber 59 to the pressure-relieved spring chamber is sealed. By turning the screw 77, the bias the valve spring 57 are adjusted.
- the pressure relief valve 55 not by changing the spring preload, but by a change in the effective effective area for the valve element acting on Pressure adjusted between two different high pressure settings.
- an auxiliary piston 58 slidably guided, corresponding to one of its guide cross-section Acting surface acted upon by the pending in the control chamber 59 pressure is.
- the guide cross section with which the Auxiliary piston 58 is guided in the screw 77 is smaller than the seat cross-section for the valve element 56.
- the pressure downstream of the nozzle 50 in the LS channel 40 as long as the pressure relief valve 55 is closed, equal to the pressure upstream the nozzle 50 is acted upon the valve element 56 at a seat cross-section corresponding active surface and opens the pressure relief valve at a low limit pressure of for example 60 bar.
- the pump pressure can then go up increase to a maximum of 70 bar: higher may be the load pressure on the third or fourth Consumers will not.
- the pressure relief valve starts to open when the at an effective effective area equal to the differential area between the seat cross section for the valve element 56 and the guide cross section of the auxiliary piston 58, acting pressure produces a force as large as the force of the valve spring 57 is.
- the after opening start flowing through the nozzle 50 Oil flow creates a pressure difference across the nozzle 50, so that after the Opening the pressure relief valve of the auxiliary piston 58 acting Pressure in the control chamber 59 is greater than the pressure in the channel 74.
- a static State is the pressure difference equal to the control ⁇ p.
- the valve element in the opening direction of a pressure force resulting from the Pressure downstream of the nozzle 50 and the seat cross section results, and in the closing direction from the low limit pressure determining force of the spring 57 and a Compressive force applied, resulting from the opposite to the pressure in the channel 74 to the control ⁇ p increased pressure in the control chamber 59 and the guide cross-section of the Hitfskolbens 58 results.
- the ratio between the guide cross section and the seat cross section 1/2 so is at a control ⁇ p of 10 bar and a lower limit pressure of 60 bar, the upper limit pressure 130 bar. With an area ratio of 1/3, the upper limit pressure is 95 bar.
- a second simple pressure relief valve 86 which is at a low limit pressure is set.
- a 2/2 way valve 60 is arranged, close by a compression spring 63 in the direction. and over the control line 64 open from the upcoming in the third LS-carial 42 pressure in the direction is charged. If the directional control valve 60 is closed, then the pressure relief valve 86 not effective. The maximum control pressure for the pressure compensator 51 and thus the maximum inlet pressure is determined by the pressure relief valve 55. If the directional control valve is opened by the pressure in the LS channel 42, then the pressure limiting valve 86 determines the maximum control pressure for the Pressure balance 51 and thus the maximum inlet pressure.
- the throttle valve For example, it responds at a pressure of 60 bar. Is activated by a or both directional control valves 30 or 31 without operation of a directional control valve 28 or 29 reaches a load pressure of 60 bar, the throttle valve 90 opens a Throttle cross-section from the control side of the pressure compensator 51 to the outlet channel 25th and keeps the pressure on the control side by the control ⁇ p under the load pressure of 60 bar, with a control ⁇ p of 10 bar, ie at 50 bar.
- the directional control valve 28 or 29 actuated, wherein the load pressure of this function is greater than 60 bar, for example 100 be bar. Upstream of the nozzle 50 are then no longer 60 bar in the LS channel 40, but 100 bar. With unchanged position of the throttle valve 90 would thus also the pressure downstream of the nozzle 50 and thus on the control side of the pressure compensator 51 increase. This would have an increase in the inlet pressure and an increase the load pressure at the controlled with the directional control valve 30 or 31 hydraulic Consumers result, for example, is at a stop.
- throttle valves used for setting the pressure levels.
- a high pressure level for the two with the directional control valves 28 and 29 controlled hydraulic Consumers a mean pressure level for the controlled with the directional control valve 30 hydraulic consumers and a low pressure level for the with the Directional valve 31 controlled hydraulic consumers provided.
- three throttle valves 90 are present, of which the high set pressure set in the directional control valve disk 16, the middle set pressure set in the directional valve disc 18 and on the low Set pressure set in the directional control valve disc 19 is housed.
- the Inputs of the throttle valves are via a leading through the directional control valves Line 92 downstream of the nozzle 50 to the LS channel 40 is connected.
- a control line 64 for the throttle valve in the directional control valve disk 16 is upstream of Nozzle 50 to the LS channel 40, the control line 64 for the throttle valve in the Directional valve disc 18 is at the LS-channel 42 and the control line 64 for the Throttling valve in the directional control valve disc 19 connected to the LS channel 43.
- the throttle valve 90 Upon actuation of the directional control valve 31, the throttle valve 90 holds the directional valve disc 19 in the same manner as described with reference to FIG Pressure on the control side of the pressure compensator 51 to such a value that the Pressure in the LS channel 43, equal to the load pressure of the corresponding hydraulic Consumer is, the low set pressure of the valve does not exceed. The load pressure is therefore limited to the low value.
- the two work other throttle valves at the medium and high pressure levels.
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Fluid-Pressure Circuits (AREA)
- Push-Button Switches (AREA)
- Measuring Fluid Pressure (AREA)
Description
- Figur 1
- ein Schaltbild des ersten Ausführungsbeispiels, bei dem der Steuerdruck durch ein einziges Druckbegrenzungsventil auf zwei durch unterschiedlich starke Federvorspannung bestimmte Werte begrenzbar ist und die Verstellung durch Umschaltung eines 2/2 Wegeventils erfolgt,
- Figur 2
- eine erste Anordnung und konstruktive Ausgestaltung des Druckbegrenzungsventils und des 2/2 Wegeventils aus Figur 1 innerhalb einer Wegeventilscheibe,
- Figur 3
- eine zweite Anordnung und konstruktive Ausgestaltung des Druckbegrenzungsventils und des 2/2 Wegeventils aus Figur 1 innerhalb einer Wegeventilscheibe,
- Figur 4
- schematisch eine weitere. Anordnung des Druckbegrenzungsventils aus Figur 3 in einem Schnitt senkrecht zu dem aus Figur 3,
- Figur 5
- ein Schaltbild des zweiten Ausführungsbeispiels, bei dem gegenüber dem ersten Ausführungsbeispiel das 2/2 Wegeventil durch ein 3/2 Wegeventil ersetzt ist,
- Figur 6
- ein Schaltbild des dritten Ausführungsbeispiels, bei dem der Steuerdruck durch ein einziges Druckbegrenzungsventil auf zwei durch unterschiedlich große Druckwirkflächen bestimmte Werte begrenzbar ist und die Verstellung durch Umschaltung eines 2/2 Wegeventils erfolgt,
- Figur 7
- die Anordnung und konstruktive Ausgestaltung des Druckbegrenzungsventils und des 2/2 Wegeventils aus Figur 6 innerhalb einer Wegeventilscheibe,
- Figur 8
- ein Schaltbild des vierten Ausführungsbeispiels, das zwei auf unterschiedlich hohe Ansprechdrücke eingestellte Druckbegrenzungsventile aufweist und bei dem das Druckbegrenzungsventil mit dem niedrigeren Ansprech druck nach dem Umschalten eins 2/2 Wegeventils wirksam werden kann,
- Figur 9
- ein. Schaltbild des fünften Ausführungsbeispiels, das wie das vierte Ausführungsbeispiel zwei Druckbegrenzungsventile und ein 2/2 Wegeventil aufweist und bei dem das Druckbegrenzungsventil mit dem niedrigeren Ansprechdruck stromab einer Düse an den zweiten Leitungsabschnitt der Lastmeldeleitung in der zweiten Wegeventilsektion angeschlossen ist und das 2/2 Wegeventil den individuellen Meldekanal der ersten Wegeventilsektion mit dem zweiten Leitungsabschnitt verbinden kann,
- Figur 10
- ein Schaltbild des sechsten Ausführungsbeispiels, bei dem im Unterschied zum fünften Ausführungsbeispiel das 2/2 Wegeventil den ersten Leitungsabschnitt der Lastmeldeleitung mit dem Eingang des Druckbegrenzungsventils mit dem niedrigeren Ansprechdruck verbinden kann,
- Figur 11
- ein Schaltbild des siebten Ausführungsbeispiels, bei dem ein auf einen hohen Ansprechdruck eingestelltes Druckbegrenzungsventil und ein von dem Druck in einem weiteren Leitungsabschnitt der Lastmeldeleitung gesteuertes Drosselventil zwischen einer Düse und dem Regelventil an den ersten Leitungsabschnitt der Lastmeldeleitung angeschlossen sind,
- Figur 12
- ein Schaltbild des achten Ausführungsbeispiels, bei dem drei auf unterschiedlich hohe Ansprechdrücke eingestellte Drosselventile vorhanden sind, und
- Figur 13
- ein Schaltbild eines Ausführungsbeispiels-, bei dem Konstantpumpe und Bypassdruckwaage durch eine load-sensing geregelte Verstellpumpe ersetzt sind.
Claims (21)
- Hydraulische Steueranordnung in Load-Sensing Technik mit einem ersten Wegeventil (28, 29), über das Druckmittel einem ersten hydraulischen Verbraucher zuführbar ist, und
mit mindestens einem weiteren Wegeventil (30, 31), über das Druckmittel einem weiteren hydraulischen Verbraucher zuführbar ist und das vorzugsweise mit dem ersten Wegeventil zu einem Ventilblock (15) zusammengefaßt ist,
mit einer Lastmeldeleitung, über die eine Steuerseite eines Load-Sensing-Regelventils (51, 53) mit einem vom höchsten Lastdruck der betätigten hydraulischen Verbraucher abhängigen Steuerdruck beaufschlagbar ist und die einen dem Regelventil (51, 53) nächsten, ersten Leitungsabschnitt (40) mit dem Steuerdruck und wenigstens einen weiteren Leitungsabschnitt (41, 42, 43) aufweist, wobei jeweils ein Leitungsabschnitt über ein Wechselventil (35, 36, 37, 38) mit dem folgenden Leitungsabschnitt oder einem individuellen Meldekanal (44, 45, 46, 47) eines Wegeventils verbindbar ist, und
mit einer Vorsteuerventilanordnung, durch die der Steuerdruck auf einen Grenzdruck begrenzt ist,
dadurch gekennzeichnet, daß die Vorsteuerventilanordnung bei einem bestimmten, in einem weiteren Leitungsabschnitt (42) der Lastmeldeleitung anstehenden Druck von einem hohen, ersten Grenzdruck auf einen niedrigeren, zweiten Grenzdruck einstellbar ist und
daß die individuellen Meldekanäle (44, 45, 46, 47), vom ersten Leitungsabschnitt (40) der Lastmeldeleitung aus betrachtet, nach fallendem maximalen Lastdruck der hydraulischen Verbraucher mit den aufeinanderfolgenden Leitungsabschnitten der Lastmeldeleitung verbindbar sind. - Hydraulische Steueranordnung nach Anspruch 1, dadurch gekennzeichnet, daß die Vorsteuerventilanordnung hydraulisch über eine Steuerleitung (64) verstellbar ist, die an den weiteren Leitungsabschnitt (42) der Lastmeldeleitung angeschlossen ist.
- Hydraulische Steueranordnung nach Anspruch 1 oder 2, dadurch gekennzeichnet, daß die Vorsteuerventilanordnung ein zwischen dem ersten Leitungsabschnitt (40) und einer Entlastungsleitung (25) angeordnetes Vorsteuerventil (55) aufweist, dessen Ansprechdruck veränderbar ist.
- Hydraulische Steueranordnung nach Anspruch 3, dadurch gekennzeichnet, daß das Vorsteuerventil ein bewegbares und von einer Ventilfeder (57) in Richtung einer Schließstellung und von einer Druckkraft an einer Wirkfläche in Richtung einer Öffnüngsstellung beaufschlagtes Ventilelement (56) aufweist und daß die Vorspannkraft der Ventilfeder (57) in Abhängigkeit von dem Druck in dem weiteren Leitungsabschnitt (42) der Lastmeldeleitung veränderbar ist.
- Hydraulische Steueranordnung nach Anspruch 4, dadurch gekennzeichnet, daß die Vorspannkraft der Ventilfeder (57) über einen Hilfskolben (58) zwischen zwei durch einen ersten ortsfesten Anschlag (77) und einen zweiten ortsfesten Anschlag (77, 81) definierten Werten veränderbar ist, daß der Hilfskolben (58) eine Wirkfläche aufweist, die größer ist als die Wirkfläche am Ventilelement (56) und die in Abhängigkeit von der durch den Druck in dem weiteren Leitungsabschnitt (42) der Lastmeldeleitung bestimmten Schaltstellung eines Umschaltventils (60, 85) von Druck entlastbar oder mit Druck beaufschlagbar ist, und daß der Hilfskolben (58) im Sinne einer Erhöhung der Federvorspannung bis zur Wirksamkeit des zweiten Anschlags (77, 81) verschiebbar ist.
- Hydraulische Steueranordnung nach Anspruch 5, dadurch gekennzeichnet, daß die zwei Anschläge (77, 81) durch zwei unabhängig voneinander justierbare Einstellschrauben gebildet sind.
- Hydraulische Steueranordnung nach Anspruch 5 oder 6, dadurch gekennzeichnet, daß die Ventilfeder (57) an dem dem Ventilelement (56) abgelegenen Ende von dem Hilfskolben (58) abstützbar ist.
- Hydraulische Steueranordnung nach Anspruch 7, dadurch gekennzeichnet, daß die Ventilfeder (57) über einen Federteller (76) an einem vorzugsweise eingeschraubten Einsatz (77) abstützbar ist, der einen von Druck entlasteten Federraum von einem in Abhängigkeit von der Stellung des Umschaltventils (60, 85) druckentlasteten oder druckbeaufschlagten Steuerraum (59) trennt, daß der Hilfskolben (58), dicht gleitend in einer Axialbohrung des Einsatzes (77) geführt, zwischen dem Federraum und dem Steuerraum (59) angeordnet ist und daß der Federteller (76) von dem Hilfskolben (58) von dem Einsatz (77) abhebbar ist.
- Hydraulische Steueranordnung nach Anspruch 8, dadurch gekennzeichnet, daß die Ventilfeder (57) über einen Federteller (76) an einem ersten verdrehbaren und den ersten Anschlag bildenden Schraubeinsatz (77) abstützbar ist, der einen von Druck entlasteten Federraum von einem in Abhängigkeit von der Stellung des Umschaltventils (60, 85) druckentlasteten oder druckbeaufschlagten Steuerraum (59) trennt, daß der Hilfskolben (58), dicht gleitend in einer Axialbohrung des Einsatzes (77) geführt, zwischen dem Federraum und dem Steuerraum (59) angeordnet ist, daß sich auf der dem Federraum abgewandten Seite des ersten Schraubeinsatzes (77) ein zweiter verdrehbarer Schraubeinsatz (81) befindet, der vorzugsweise von außen verstellbar ist und der den zweiten, vom Hilfskolben (58) beaufschlagbaren Anschlag bildet.
- Hydraulische Steueranordnung nach Anspruch 3, dadurch gekennzeichnet, daß das Vorsteuerventil (55) ein bewegbares und von einer Ventilfeder (57) in Richtung einer Schließstellung beaufschlagtes Ventilelement (56) aufweist, daß das Ventilelement (56) durch einen im ersten Leitungsabschnitt (40) der Lastmeldeleitung stromab einer Düse (50) und an einer ersten Steuerfläche anstehenden Druck in Öffnungsrichtung beaufschlagbar ist und daß eine zweite Steuerfläche an einem Hilfskolben (58) vorhanden ist, der auf das Ventilelement (56) wirkt und der in Abhängigkeit von der durch den Druck in dem weiteren Leitungsabschnitt (42) der Lastmeldeleitung bestimmten Schaltstellung eines Umschaltventils (60) von Druck entlastet oder mit Druck beaufschlagbar ist.
- Hydraulische Steueranordnung nach Anspruch 10, dadurch gekennzeichnet, daß das Ventilelement (56) durch einen an der zweiten Steuerfläche anstehenden Druck in Schließstellung beaufschlagt ist und daß die zweite Steuerfläche kleiner als die erste Steuerfläche ist.
- Hydraulische Steueranordnung nach Anspruch 11, dadurch gekennzeichnet, daß ein von Druck entlasteter Federraum des Vorsteuerventils (55) durch einen zur Veränderung der Vorspannung der Ventilfeder (57) vorzugsweise verstellbaren Einsatz (77) gegen einen je nach Schaltstellung des Umschaltventils (60) von Druck entlasteten oder mit Druck beaufschlagten Steuerraum (59) abgedichtet ist und daß ein am Ventilelement (56) anliegender oder fest verbundener Hilfskolben (58) mit einer Querschnittsfläche, die kleiner als die erste Steuerfläche ist, dicht gleitend in einer zu dem Steuerraum (59) hin offenen Bohrung des Einsatzes (77) geführt ist.
- Hydraulische Steueranordnung nach einem der Ansprüche 5 bis 12, dadurch gekennzeichnet, daß das Umschaltventil ein 2/2 Wegeventil (60) ist und in Reihe mit einer Düse (61) zwischen der Lastmeldeleitung und einer Entlastungsleitung (25) angeordnet ist und daß der Steuerraum (59) am Hilfskolben (58) an die Verbindung zwischen Düse (61) und 2/2 Wegeventil (60) angeschlossen ist.
- Hydraulische Steueranordnung nach einem der Ansprüche 5 bis 12, dadurch gekennzeichnet, daß das Umschaltventil ein 3/2 Wegeventil (85) ist und einen Steuerraum (59) am Hilfskolben (58) in der einen Schaltstellung mit der Lastmeldeleitung und in der anderen Schaltstellung mit einer Entlastungsleitung (25) verbindet.
- Hydraulische Steueranordnung nach Anspruch 1 oder 2, dadurch ge kennzeichnet, daß die Vorsteuerventilanordnung ein erstes, zwischen dem ersten Leitungsabschnitt (40) und einer Entlastungsleitung (25) angeordnetes oder dazwischen schaltbares Vorsteuerventil (55, 90) und ein zweites, zwischen der Lastmeldeleitung und der Entlastungsleitung (25) angeordnetes oder dazwischen schaltbares Vorsteuerventil (86, 90) aufweist und daß der Ansprechdruck des zweiten Vorsteuerventils (86, 90) kleiner als der Ansprechdruck des ersten Vorsteuerventils (55, 90) ist.
- Hydraulische Steueranordnung nach Anspruch 15, dadurch gekennzeichnet, daß beide Vorsteuerventile Druckbegrenzungsventile (55, 86) sind und daß das zweite Vorsteuerventil (86) mit seinem Eingang über ein in Abhängigkeit von dem in einem weiteren Leitungsabschnitt (42) der Lastmeldeleitung anstehenden Druck schaltbaren Umschaltventil (60) mit dem ersten Leitungsabschnitt (40) verbindbar ist.
- Hydraulische Steueranordnung nach Anspruch 16, dadurch gekennzeichnet, daß das zweite Vorsteuerventil (86) mit seinem Eingang stromab einer Düse (87) mit einem ersten weiteren Leitungsabschnitt (41) verbunden ist und daß das Umschaltventil (60) in Abhängigkeit von dem in einem dem ersten weiteren Leitungsabschnitt (41) nach hinten folgenden weiteren Leitungsabschnitt (42) anstehenden Druck den ersten Leitungsabschnitt (40) oder einen mit diesem verbindbaren individuellen Meldekanal (44) stromab einer darin befindlichen Düse (50, 88) mit dem Eingang des zweiten Vorsteuerventils (86) verbindet oder davon trennt.
- Hydraulische Steueranordnung nach Anspruch 15, dadurch gekennzeichnet, daß das zweite Vorsteuerventil (90) zwischen dem ersten Leitungsabschnitt (40) und einer Entlastungsleitung (25) angeordnet ist und daß sein bewegliches Ventilelement in Schließrichtung von einer Ventilfeder (91) und in Öffnungsrichtung von dem in dem weiteren Leitungsabschnitt (42, 43) anstehenden Druck beaufschlagbar ist.
- Hydraulische Steueranordnung nach einem vorhergehenden Anspruch, dadurch gekennzeichnet, daß die Vorsteuerventilanordnung örtlich einem Wegeventil (28) mit einfach wirkender Funktion zugeordnet ist.
- Hydraulische Steueranordnung nach Anspruch 19, dadurch gekennzeichnet, daß das Vorsteuerventil (55) mit seiner Achse in oder parallel zu einer durch die Achse des Wegeventils (28) und eine Arbeitsanschluß aufgespannten Ebene, vorzugsweise parallel zur Achse des Wegeventils angeordnet ist.
- Hydraulische Steueranordnung nach Anspruch 20, dadurch gekennzeichnet, daß das Umschaltventil (60) mit seiner Achse senkrecht zu der Ebene angeordnet ist.
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE10216119 | 2002-04-12 | ||
DE10216119A DE10216119A1 (de) | 2002-04-12 | 2002-04-12 | Hydraulische Steueranordnung in Load-Sensing Technik |
PCT/EP2003/003537 WO2003087585A1 (de) | 2002-04-12 | 2003-04-04 | Hydraulische steueranordnung in load-sensing technik |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1497559A1 EP1497559A1 (de) | 2005-01-19 |
EP1497559B1 true EP1497559B1 (de) | 2005-12-21 |
Family
ID=28458747
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP03724956A Expired - Lifetime EP1497559B1 (de) | 2002-04-12 | 2003-04-04 | Hydraulische steueranordnung in load-sensing technik |
Country Status (6)
Country | Link |
---|---|
US (1) | US20050178116A1 (de) |
EP (1) | EP1497559B1 (de) |
JP (1) | JP2006505746A (de) |
AT (1) | ATE313715T1 (de) |
DE (2) | DE10216119A1 (de) |
WO (1) | WO2003087585A1 (de) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102013220750A1 (de) * | 2013-10-15 | 2015-04-16 | Robert Bosch Gmbh | Ventilblock mit einer Ventilanordnung |
Families Citing this family (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB2446157B (en) * | 2007-02-02 | 2011-06-15 | Paul John Brooks | A Shuttle Valve Assembly |
CN101629588B (zh) * | 2009-06-01 | 2011-11-09 | 中国航空工业集团公司西安飞机设计研究所 | 一种双控口液控阀 |
DE102010009705A1 (de) * | 2010-03-01 | 2011-09-01 | Robert Bosch Gmbh | Hydraulische Steueranordnung |
WO2016143167A1 (ja) * | 2015-03-11 | 2016-09-15 | Kyb株式会社 | 流体圧制御装置 |
JP6909164B2 (ja) * | 2018-01-12 | 2021-07-28 | Kyb株式会社 | 流体圧制御装置 |
JP7095589B2 (ja) * | 2018-12-26 | 2022-07-05 | 株式会社豊田自動織機 | 産業車両の油圧駆動装置 |
DE102020209387B3 (de) | 2020-07-24 | 2021-07-15 | Hawe Hydraulik Se | Vorwahlventil, Hydraulikventilverband und Hydrauliksteuervorrichtung |
US11680381B2 (en) * | 2021-01-07 | 2023-06-20 | Caterpillar Underground Mining Pty. Ltd. | Variable system pressure based on implement position |
Family Cites Families (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
SE371259B (de) * | 1972-10-05 | 1974-11-11 | Tico Ab | |
DE3420674C2 (de) * | 1984-06-02 | 1986-10-02 | Danfoss A/S, Nordborg | Druckversorgungseinrichtung für ein Hydrauliksystem |
DE3535771A1 (de) * | 1985-10-07 | 1987-04-09 | Linde Ag | Hydrostatischer antrieb mit mehreren verbrauchern |
US4977928A (en) * | 1990-05-07 | 1990-12-18 | Caterpillar Inc. | Load sensing hydraulic system |
DE19715021A1 (de) * | 1997-04-11 | 1998-10-15 | Rexroth Mannesmann Gmbh | Hydraulische Steueranordnung zur Druckmittelversorgung eines ersten und eines zweiten hydraulischen Verbrauchers |
JP2001323902A (ja) * | 2000-05-16 | 2001-11-22 | Hitachi Constr Mach Co Ltd | 油圧駆動装置 |
-
2002
- 2002-04-12 DE DE10216119A patent/DE10216119A1/de not_active Withdrawn
-
2003
- 2003-04-04 DE DE50302004T patent/DE50302004D1/de not_active Expired - Lifetime
- 2003-04-04 US US10/509,991 patent/US20050178116A1/en not_active Abandoned
- 2003-04-04 JP JP2003584505A patent/JP2006505746A/ja active Pending
- 2003-04-04 WO PCT/EP2003/003537 patent/WO2003087585A1/de active IP Right Grant
- 2003-04-04 AT AT03724956T patent/ATE313715T1/de not_active IP Right Cessation
- 2003-04-04 EP EP03724956A patent/EP1497559B1/de not_active Expired - Lifetime
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102013220750A1 (de) * | 2013-10-15 | 2015-04-16 | Robert Bosch Gmbh | Ventilblock mit einer Ventilanordnung |
US9874884B2 (en) | 2013-10-15 | 2018-01-23 | Robert Bosch Gmbh | Valve block having a valve assembly |
Also Published As
Publication number | Publication date |
---|---|
DE50302004D1 (de) | 2006-01-26 |
EP1497559A1 (de) | 2005-01-19 |
ATE313715T1 (de) | 2006-01-15 |
US20050178116A1 (en) | 2005-08-18 |
JP2006505746A (ja) | 2006-02-16 |
WO2003087585A1 (de) | 2003-10-23 |
DE10216119A1 (de) | 2003-10-23 |
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