EP1911979B1 - Dynamische Fluidvorrichtung - Google Patents

Dynamische Fluidvorrichtung Download PDF

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Publication number
EP1911979B1
EP1911979B1 EP06021319A EP06021319A EP1911979B1 EP 1911979 B1 EP1911979 B1 EP 1911979B1 EP 06021319 A EP06021319 A EP 06021319A EP 06021319 A EP06021319 A EP 06021319A EP 1911979 B1 EP1911979 B1 EP 1911979B1
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EP
European Patent Office
Prior art keywords
pump
sliding chamber
user
fluid device
dynamic fluid
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.)
Active
Application number
EP06021319A
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English (en)
French (fr)
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EP1911979A1 (de
Inventor
Eronne Mamei
Enrico Mamei
Omer Mamei
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Studio Tecnico 6M SRL
Original Assignee
Studio Tecnico 6M SRL
Priority date (The priority date 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 date listed.)
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Publication date
Application filed by Studio Tecnico 6M SRL filed Critical Studio Tecnico 6M SRL
Priority to DK06021319.6T priority Critical patent/DK1911979T3/da
Priority to SI200631185T priority patent/SI1911979T1/sl
Priority to EP06021319A priority patent/EP1911979B1/de
Priority to AT06021319T priority patent/ATE521813T1/de
Publication of EP1911979A1 publication Critical patent/EP1911979A1/de
Application granted granted Critical
Publication of EP1911979B1 publication Critical patent/EP1911979B1/de
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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
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/0401—Valve members; Fluid interconnections therefor
    • F15B13/0402—Valve members; Fluid interconnections therefor for linearly sliding valves, e.g. spool 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
    • 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
    • F15B11/163—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load for sharing the pump output equally amongst users or groups of users, e.g. using anti-saturation, pressure compensation
    • 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
    • F15B11/17—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors using two or more pumps
    • 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
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/20576—Systems with pumps with multiple pumps
    • 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
    • F15B2211/40—Flow control
    • F15B2211/415—Flow control characterised by the connections of the flow control means in the circuit
    • 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
    • F15B2211/40—Flow control
    • F15B2211/45—Control of bleed-off flow, e.g. control of bypass flow to the return line
    • 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

Definitions

  • the present invention refers to a dynamic fluid device.
  • Hydraulic pumps with a fixed flow rate have the advantage of being considerably more economical than those with a variable flow rate which are also known and widely used.
  • main functions we mean those functions the machine needs to move safely, for example, hydralic powered steeannular
  • secondary functions we mean those operating functions machines can be equipped with for working, for example, a hydraulic lifting equipment, a bucket and the like.
  • the pumps with a fixed flow rate must be sized to guarantee a sufficient flow of pressurised oil under the heaviest conditions, i.e. when a great number of the primary and secondary equipments are being used simultaneously.
  • the pump When this does not occur, i.e. when only one user apparatus is used, the pump, sized to supply a flow to meet the heaviest conditions, continues to supply the same flow of pressurised oil which becomes noticeably much more than what is really needed to operate a single user apparatus; consequently, a large part of the pressurised oil flow supplied by the pump is superfluous and, for this reason, sent to a discharge point of the hydraulic system provided for.
  • hydraulic circuits are used equipped with two pumps with a predefined fixed flow rate and installed in parallel with each other; each pump is connected by a pipe to a single first user means and a single second user means.
  • An extension of the feed pipes is provided for at the output of both the first and second user means that join together to flow into one single additional pipe which, in turn, is connected to a third user means; the sum of the flows of the single pumps when they are both working comes together in this one single additional pipe.
  • a solenoid valve is mounted on one of the feed pipe extensions, before they join together, which opens or closes the extension it is mounted on, alternatively letting the flow of oil go through this extension to the third user means together with the flow of oil that goes through the parallel pipe of the other user means, or deviating the flow of the pipe extension on which it is mounted to a discharge contemplated for this purpose in the hydraulic circuit.
  • a second known hydraulic system to supply user means uses just one pump, normally a gear pump which, by means of a pipe, is connected to a distributor unit intended to distribute pressurised oil on demand to a multitude of user means.
  • the oil is distributed when requested in order to work one or more user means and the request for oil is activated either by a manual operation of a users means' driving unit mounted on a machine by an operator or by an automatic device designed for this purpose on the distributor.
  • a valve is installed between the gear pump and distributor that connects the oil feeding pipe, adjusting the passage hole through which the oil flows to a discharge.
  • the valve is controlled by pressure signals that reach it by way of a pressure detecting pipe which in technical jargon is called a "load-sensing line"; pressure is detected inside the distributor and transmitted to the valve which, according to the specific requirements of pressurised oil modifies the passage hole to the distributor and, hence, the available flow of pressurised oil to the user means; when no signal is sent by the load-sensing line, the valve normally keeps the feed pipe connected to the discharge and all the pump flow goes into it.
  • a first drawback is that the hydraulic circuits that have pumps with a fixed flow rate feeding single user means do not allow for priority in feeding such units.
  • a second drawback is that if, in a hydraulic circuit which has two pumps in parallel with each other, one of the pumps is damaged, the user means being supplied by this damaged pump cannot work .
  • a third drawback is that if a third user means requires a reduced flow of pressurised oil to work compared to the flow rate just one of the pumps installed in parallel on the hydraulic circuit can supply, a significant quantity of pressurised oil has to be discharged and the energy spent to operate the pump, or both pumps, is lost.
  • a drive system comprising a plurality of hydraulic actuators which are driven by the hydraulic fluid supplied by two pumps, and a valve arrangement which is arranged between the pumps and the actuators for selectively connecting them, by controlling the flow of the hydraulic fluid from the pumps to the hydraulic actuators.
  • a valve arrangement which is arranged between the pumps and the actuators for selectively connecting them, by controlling the flow of the hydraulic fluid from the pumps to the hydraulic actuators.
  • the technical aim of the invention is to improve the state of the technique.
  • One object of the invention is to make a dynamic fluid device allowing to limit the losses of energy spent to feed pressurised oil to the work vehicle user means that require low oil rates of flow.
  • Another object of the invention is to make a dynamic fluid device allowing to feed work vehicle user means according to a predetermined priority.
  • Yet another object of the invention is to make a dynamic fluid device allowing to feed work vehicle user means also when one of the pumps that supplies parallel flows of pressurised oil shuts down due to a failure.
  • Another object of the invention is to make a dynamic fluid device that can be installed on already existing hydraulic circuits and used on work vehicles.
  • the above objects are achieved by the dynamic fluid device comprising all the features recited by independent claim 1.
  • the dynamic fluid device does, therefore, allow to send predefined rates of flow of pressurised oil to machine user devices according to pre-established requests and also according to pre-established priorities, thus noticeably reducing the amount of energy lost to operate the sources that supply machine user means with pressurised oil. Further characteristics and advantages of the present invention will appear even more evident from the description of a form of embodiment of a dynamic fluid device illustrated by way of non limiting example in the accompanying drawings, wherein:
  • 1 indicates a dynamic fluid device as a whole which comprises first pumping means 2 and second pumping means 3 arranged in parallel with each other to pump a pressurised fluid - which is oil in this specific case - to three user points or user means that are operable with pressurised oil and which are schematically indicated in the figures with PR1, PR2 and EF respectively, and more specifically, with PR1 the first user means, with PR2 the second user means and with EF the third user means.
  • the dynamic fluid device 1 also comprises distributor means 4 that are interposed amongst said first pumping means 2, second pumping means 3 and user means PR1, PR2 and EF and connected to them with connection means, for example, annular-shaped connection holes, a first hole 5, fifth hole 6, a sixth hole 7 respectively.
  • connection means for example, annular-shaped connection holes, a first hole 5, fifth hole 6, a sixth hole 7 respectively.
  • the first pumping means 2 and the second pumping means 3 each comprise their own first pump 8 and second pump 9, both with a fixed flow rate that, through the respective first connection hole 5 and second connection hole 11, controlled by respective one-way valves 12 and 13, send pressurised oil to the distributor means 4.
  • the latter comprise a body 14 in which at least one sliding chamber 15 is made and into which the connection holes 5, 6, 7 and 11 flow; besides these, a third connection hole 16 and a fourth connection hole 17 are contemplated that connect the sliding chamber 15 with, respectively, two discharge means indicated in the drawings by arrows "S1" and "S2".
  • the sliding chamber 15 is cylindrical in shape and features a first end 115 closed with a plug 18 and an opposing second end 215 closed with contrast means 19 described more in detail further on.
  • the distributor means 4 also comprises a distributor element 20 sliding in the sliding chamber 15 and which is intended, slidingly accomodated inside it, to open and shut all the connection holes 5, 6, 7, 11, 16, 17 according to a predetermined sequence; slides of the distributor element 20 occurs by overcoming the action of the contrast means 19.
  • the distributor element 20 comprises a cylindrical body 21 axially crossed by a through conduit 22; this has a third open end 122 that faces the plug 18 and an opposing fourth end 222 that features first crosswise openings 23 flowing into the sliding chamber 15 and which are obtained in the cylindrical body 21; the through conduit 22 also has second crosswise openings 24 flowing into the sliding chamber 15 which are obtained in the cylindrical body 21 in a position between the first crosswise openings 23 and the third end 122, substantially by the first hole 5.
  • the first user means PR1 are connected to the first pump 8 and also to the second pump 9 by means of an intermediate conduit 111 obtained inside the body 14 and which connects the second pump 9 to the first pump 8.
  • the cylindrical body 21 features at least three perimeter grooves created in succession: a first groove 25 is arranged to connect, by means of the sliding of the cylindrical body 21, the second connection hole 11 and the fourth connection hole 17 together, a second groove 26 is arranged to connect, between the first connection hole 5 and the third connection hole 16, a third groove 27 is provided to connect the first hole 5 and the sixth hole 7 together.
  • the second crosswise holes 24 open into the third groove 27 while the first crosswise holes 23 are provided to connect, according the slidings of the cylindrical body 21, the through conduit 22 with the fifth annular-shaped hole 6.
  • the contrast means 19 comprises a plug element 28 that can be screwed into the second end 215 of the sliding chamber 15.
  • a first housing 29 is defined inside the plug element 28, created axially and inside which a return spring 30 is housed, contained between the bottom 129 of the first housing 29 and the opposing second concave housing 31 obtained in the fourth end 222.
  • a detecting line between the sliding chamber 15 and the user means PR1, PR2 and EF detects the pressure inside the latter, known by the term "load-sensing line", by means of which a signal indicated with “LS” flows into the sliding chamber 15 through a connecting conduit 33 created in the body 14.
  • the load-sensing signal "LS" corresponds to the strongest of the “LS1", “LS2”, and “LS3” signals because all the load-sensing signals “LS1”, “LS2”, “LS3” go towards the first valve means 35 and second valve means 36: more precisely, the load-sensing signals "LS2" and “LS3” reach the second valve means 36 coming from the second user means PR2 and third user means EF, the strongest of which goes through the second valve means 36, closing passage to the other signal and, through a line 10, flows to the first valve means 35 where the load-sensing signal "LS1" also flows, coming from the first user means PR1.
  • the strongest signal goes through the first valve means 35 which consequently close passage to the other signal.
  • the resulting "LS" signal reaches the first housing 29 through the connecting conduit 33 and acts jointly with the spring 30 on the surface of the second concave housing 31.
  • a radial opening 37 is made in the second concave housing 31 which, when the cylindrical body 21 slides along, opens or closes, aligning itself with a seventh annular-shaped hole 38 which, in this second version, is created in the body 14, between the connecting conduit 33 and the fifth hole 6.
  • the seventh annular-shaped hole 38 is connected to a storage or drainage tank 39 with the interposition of third valve means 40 that are normally closed, and opened when the pressure inside the annular-shaped hole 38 reaches an established limit value: more specifically, the third valve means 40 acts as a so called "over-pressure safety relief valve".
  • Additional fourth valve means 41 comprising another "over-pressure safety relief valve", completely identical to the previous one, is interposed between the tank 39 and the first hole 5 and also these fourth valve means 41 are normally closed and opened when the pressure inside the first hole 5 reaches a predetermined limit value.
  • Fifth valve means 42 are also contemplated between the first hole 5 and the first user means PR1, and are normally open, as can be seen in Figures 19 and 12 ; these fifth valve means 42 is provided to protect the first user means PR1 against excessive pressure values, closing the passage of oil towards it.
  • Figure 8 illustrates the configuration that occurs when a motor is turned on that operates the first pump 8 and the second pump 9 and when none of the user means PR1, that could coincide for example with the driving devices of a vehicle, PR2, that could correspond to the braking system of a vehicle, and EF, that could correspond to a working tool of a vehicle, require a flow of oil.
  • the cylindrical body 21 remains balanced inside the sliding chamber 15 between the force exerted by the contrast means 19 and the pressure of the oil that is taking up the space 34 and which is pushing against the third end 122 of the body 21; with the body 21 in this position the second pump 9 is connected to the discharge means S2 through the first groove 25, and it's just the first pump 8 that sends oil to the user means PR1, PR2 and
  • a "load-sensing" signal "LS" is generated which, through the connecting conduit 33, reaches the first housing 29 and acts by pressing on the second concave housing 31, summing its own force with that of the spring 30.
  • the "LS" signal that acts on the second concave housing 31 coincides with the strongest of the "LS1", "LS2" and "LS3" signals that pass through the second valve means 36 and the first valve means 35.
  • the "load-sensing" signal continues to act on the concave housing 31, still moving the cylindrical body 21 in the direction of the plug 18 and gradually reaching the configuration illustrated in Figure 6 .
  • both the first pump 8 and the second pump 9 send their flows of oil to the user means PR1, PR2 and EF because as the cylindrical body 21 moves, the fourth hole 17 closes and the connection between the first groove 25 and the latter, and therefore to the discharge means S2, is interrupted.
  • the cylindrical body 21, moving starts feeding the first user means PR1, the second user means PR2 and the third user means EF according to a predetermined priority.
  • the sixth hole 7 is completely closed and the third user means is no longer fed; therefore, the whole flow of the first pump 8 and of the second pump 9 is sent only to the second user means PR2 and the first user means PR1, having priority over the third user means EF.
  • the flows of the first pump 8 and of the second pump 9 mainly reach the first user means PR1, giving it priority in the supply of oil, while a limited flow reaches the second user means PR2.
  • the cylindrical body 21 continues moving towards the plug 18, reaching the configuration illustrated in Figure 1 where the connection between the first crosswise openings 23 and the fifth hole 6 is completely closed and the flows of pressurised oil supplied both by the first pump 8 and the second pump 9 are sent to the user means PR1 only.
  • the fourth valve means 41 are calibrated so as to connect the first hole 5 and the tank 39 together when the pressure inside the first hole 5 reaches values that are too high, for example, caused by an anomalous interruption in sliding of the cylindrical body 21, to avoid damaging the first pump 8 or the second pump 9.
  • this pressure value reaches and exceeds a predetermined opening limit value of the third valve means 40, it opens and places the storage tank 39 in connection with the first housing 29, discharging the pressure in it and causing the cylindrical body 21 to move in the direction of the contrast means 19 to such an extent that the connection opens between the second pump 9 and the discharge means S2, through the first groove 25 which is across the second hole 11 and the fourth hole 17.
  • the pressure inside the first hole 5 reaches a predefined limit value coinciding with the opening value of the third valve means 41, it will open and place the first hole 5 in connection with the storage tank 39, discharging the pressure into it until the closing value is reached for the third valve means 41.
  • the fifth valve means 42 receive the thrust produced by an elastic element 45 that has a preselected load, and by the same LS1 pressure signal which is detected inside the first user means PR1, through a corresponding derived line 43.
  • the fifth valve means 42 receive the same thrust produced by the pressure of the oil that flows towards the first user means PR1, through a second derived line 44.
  • the fifth valve means 42 positions itself in the oil passage closed configuration, thus protecting the first user means PR1 from possible damage caused by an excessively high pressure value.

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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)
  • Transition And Organic Metals Composition Catalysts For Addition Polymerization (AREA)
  • Reciprocating Pumps (AREA)
  • Filling Or Discharging Of Gas Storage Vessels (AREA)

Claims (14)

  1. Dynamische Fluidvorrichtung (1), die aufweist:
    eine erste Pumpeinrichtung (2) und eine zweite Pumpeinrichtung (3), die parallel zueinander angeordnet sind, um ein unter Druck stehendes Fluid zu Verbrauchereinrichtungen (PR1, PR2, EF) zu pumpen; und
    eine Verteilereinrichtung (4), die zwischen die erste Pumpeinrichtung (2), die dritte Pumpeinrichtung (3) und die Verbrauchereinrichtungen (PR1, PR2, EF) geschaltet ist und mit ihnen über Verbindungseinrichtungen verbunden ist,
    bei der die Verteilereinrichtung (4) so angeordnet ist, dass sie einzeln und/oder gemeinsam und/oder gemäß zuvor bestimmten Reihenfolgen die erste Pumpeinrichtung (2) und/oder die zweite Pumpeinrichtung (3) mit den Verbrauchereinrichtungen (PR1, PR2, EF) verbindet, und aufweist:
    eine Körpereinrichtung (14), in der mindestens eine Gleitkammer (15) bereitgestellt wird, versehen mit verbindungslöchern (5, 6, 7, 11, 16, 17) bzw. mit den Verbrauchereinrichtungen (PR1, PR2, EF), mit der ersten Pumpeinrichtung (2) und der zweiten Pumpeinrichtung (3) und mit den Austrittseinrichtungen (S1, S2);
    ein Verteilerelement (20), das gleitend von der Gleitkammer (15) aufgenommen wird und geeignet ist, durch Gleiten die Verbindungslöcher (5, 6, 7, 11, 16, 17) zu öffnen und zu schließen; und
    eine Abhebeeinrichtung (19) für das Gleiten des Verteilerelements (20) in der Gleitkammer (15),
    bei der die Gleitkammer (15) zylindrisch geformt ist und ein erstes Ende (115), das durch eine Stopfeneinrichtung (18) verschlossen wird, und ein gegenüberliegendes zweites Ende (215), das durch die Abhebeeinrichtung (19) verschlossen wird, besitzt und
    bei der das Verteilerelement (20) einen zylindrischen Körper (21) aufweist, der axial von einem durchgehenden Kanal (22) gekreuzt wird, der ein der Stopfeneinrichtung (18) zugewandtes, drittes offenes Ende (122) und ein gegenüberliegendes viertes Ende (222) hat,
    wobei die dynamische Fluidvorrichtung (1) dadurch
    gekennzeichnet ist, dass die Abhebeeinrichtung (19) aufweist:
    ein Stopfenelement (28), das in das zweite Ende (215) der Gleitkammer (15) geschraubt werden kann;
    ein erstes Gehäuse (29), das axial im Stopfenelement (28) gebildet wird;
    eine elastische Abhebeeinrichtung (30), die in das erste Gehäuse (29) eingesetzt ist und zwischen einer Unterseite (129) desselben und einem zweiten konkaven Gehäuse (31), gegenüber dem ersten Gehäuse (29) und im vierten Ende (222) des durchgehenden Kanals (22) bereitgestellt, enthalten ist.
  2. Dynamische Fluidvorrichtung (1) gemäß Anspruch 1, bei der die Verbrauchereinrichtungen (PR1, PR2, EF) entsprechende Einspeiseprioritäten haben, dadurch gekennzeichnet, dass die Verteilereinrichtung (4) so gestaltet ist, dass sie je nach den vorher bestimmten Reihenfolgen die erste Pumpeinrichtung (2) und die zweite Pumpeinrichtung (3) mit den Verbrauchereinrichtungen (PR1, PR2, EF) verbindet, während sie die entsprechenden Einspeiseprioritäten einhält.
  3. Dynamische Fluidvorrichtung (1) gemäß Anspruch 1 oder 2, bei der die erste Pumpeinrichtung (2) und die zweite Pumpeinrichtung (3) eine erste Pumpe (8) bzw. eine zweite Pumpe (9), beide mit nicht veränderbarer Fördermenge, aufweisen.
  4. Dynamische Fluidvorrichtüng (1) gemäß einem der Ansprüche 1 bis 3, bei der die Verbindungskanäle in den Körpereinrichtungen (14), zwischen den Verbrauchereinrichtungen (PR1, PR2, EF) und der Gleitkammer (15) und zwischen der ersten Pumpe (8) und der zweiten Pumpe (9) und der Gleitkammer (15) bereitgestellt werden.
  5. Dynamische Fluidvorrichtung (1) gemäß einem der Ansprüche 1 bis 4, bei der das gegenüberliegende vierte Ende (222) des durchgehenden Kanals (22) erste über Kreuz angeordnete Öffnungen (23) besitzt, die sich in die Gleitkammer (15) hinein öffnen, und bei der zweite über Kreuz angeordnete Öffnungen (24), die sich in die Gleitkammer (15) hinein öffnen, zwischen den ersten über Kreuz angeordneten Öffnungen (23) und dem dritten offenen Ende (122) des durchgehenden Kanals (22) bereitgestellt werden.
  6. Dynamische Fluidvorrichtung (1) gemäß einem der Ansprüche 1 bis 5, bei der die Verbindungslöcher (5, 6, 7, 11, 16, 17) aufweisen:
    ein erstes ringförmiges Verbindungsloch (5) zwischen der Gleitkammer (15) und der ersten Pumpe (8),
    ein zweites ringförmiges Verbindungsloch (11) zwischen der Gleitkammer (15) und der zweiten Pumpe (9),
    ein drittes ringförmiges Verbindungsloch (16) zwischen der Gleitkammer (15) und den Austrittseinrichtungen (S1, S2),
    ein viertes ringförmiges Verbindungsloch (17) zwischen der Gleitkammer (15) und den Äustrittseinrichtungen (S1, S2),
    ein fünftes ringförmiges Verbindungsloch (6) zwischen der Gleitkammer (15) und der zweiten Verbrauchereinrichtung (PR2) der Verbrauchereinrichtungen (PR1, PR2, EF),
    ein sechstes ringförmiges Verbindungsloch (7) zwischen der Gleitkammer (15) und der dritten Verbrauchereinrichtung (EF) der Verbrauchereinrichtungen (PR1, PR2, EF),
  7. Dynamische Fluidvorrichtung (1) gemäß einem der Ansprüche 1 bis 6, bei der die erste Verbrauchereinrichtung (PR1) der Verbrauchereinrichtungen (PR1, PR2, EF) mit der ersten Pumpe (8) und der zweiten Pumpe (9) verbunden ist.
  8. Dynamische Fluidvorrichtung (1) gemäß einem der Ansprüche 1 bis 7, bei welcher der zylindrische Körper (21) mindestens drei über den Umfang verlaufende Nuten (25, 26, 27) aufweist, die hintereinander auf der äußeren Oberfläche des zylindrischen Körpers (21) gebildet werden,
    wobei eine erste Nut (25) von ihnen bereitgestellt wird, um durch das Gleiten des zylindrischen Körpers (21) in der Gleitkammer (15) das zweite Verbindungsloch (11) und das vierte Verbindungslöch (17) miteinander zu verbinden,
    wobei eine zweite Nut (26) bereitgestellt wird, um durch das besagte Gleiten das erste Verbindungsloch (5) und das dritte Verbindungsloch (16) miteinander zu verbinden, und
    wobei eine dritte Nut (27) bereitgestellt wird, um durch das besagte Gleiten das erste Loch (5) und das sechste Loch (7) miteinander zu verbinder.
  9. Dynamische Fluidvorrichtung (1) gemäß Anspruch 5, bei der die zweiten über Kreuz angeordneten Löcher (24) sich in die dritte Nut (27) hinein öffnen.
  10. Dynamische Fluidvorrichtung (1) gemäß Anspruch 5, bei der die ersten über Kreuz angeordneten Löcher (23) des durchgehenden Kanals (22) bereitgestellt werden, um durch das Gleiten des zylindrischen Körpers (21) des Verteilerelements (20) den durchgehenden Kanal (22) mit dem sechsten Loch (7) zu verbinden.
  11. Dynamische Fluidvorrichtung (1) gemäß Anspruch 1, bei der das Stopfenelement (28) in das zweite Ende (215) der Gleitkammer (15) geschraubt werden kann.
  12. Dynamische Fluidvorrichtung (1) gemäß Anspruch 1, bei der das zweite konkave Gehäuse (31) mit verbindenden radialen Öffnungen (37) zum Verbinden mit einem entsprechenden siebenten Loch (38), das in der Körpereinrichtung (14) hergestellt wurde, versehen ist, wobei das siebente Loch (38) mit einem Speicherbehälter (39) verbunden ist.
  13. Dynamische Fluidvorrichtung (1) gemäß einem der Ansprüche 1 bis 12, bei der zwischen der Gleitkammer (15) und den Verbrauchereinrichtungen (PR1, PR2, EF) ein Rohr (LS; LS1; LS2; LS3) zum Detektieren des Drucks in den Verbrauchereinrichtungen (PR1, PR2, EF), das unter der Bezeichnung "Load-Sensing-Leitung" bekannt ist, bereitgestellt wird, wobei das Rohr sich in die Nähe des zweiten Endes (215) der Gleitkammer (15) mit einem Verbindungskanal (33) öffnet.
  14. Dynamische Fluidvorrichtung (1) gemäß Anspruch 1 oder 2, bei der die erste Pumpeinrichtung (2) und die zweite Pumpeinrichtung (3) eine erste Pumpe (8) bzw. eine zweite Pumpe (9), mindestens eine von ihnen mit nicht veränderbarer Fördermenge und die andere mit veränderbarer Fördermenge, aufweisen.
EP06021319A 2006-10-11 2006-10-11 Dynamische Fluidvorrichtung Active EP1911979B1 (de)

Priority Applications (4)

Application Number Priority Date Filing Date Title
DK06021319.6T DK1911979T3 (da) 2006-10-11 2006-10-11 Dynamisk fluidanordning
SI200631185T SI1911979T1 (sl) 2006-10-11 2006-10-11 Dinamična fluidna naprava
EP06021319A EP1911979B1 (de) 2006-10-11 2006-10-11 Dynamische Fluidvorrichtung
AT06021319T ATE521813T1 (de) 2006-10-11 2006-10-11 Dynamische fluidvorrichtung

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP06021319A EP1911979B1 (de) 2006-10-11 2006-10-11 Dynamische Fluidvorrichtung

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EP1911979A1 EP1911979A1 (de) 2008-04-16
EP1911979B1 true EP1911979B1 (de) 2011-08-24

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EP (1) EP1911979B1 (de)
AT (1) ATE521813T1 (de)
DK (1) DK1911979T3 (de)
SI (1) SI1911979T1 (de)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2011044870A1 (de) * 2009-10-12 2011-04-21 Ixetic Bad Homburg Gmbh Hydraulikpumpenanordnung
CN103790883B (zh) * 2014-01-25 2016-04-13 中国北方车辆研究所 一种双泵流量分配控制阀

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5220088Y2 (de) * 1972-07-15 1977-05-10
US4002027A (en) * 1973-10-01 1977-01-11 Tyrone Hydraulics, Inc. Multiple pump control system
DE3823892C2 (de) * 1988-07-14 2001-07-26 Bosch Gmbh Robert Hydraulikanlage mit zwei Pumpen
US6205780B1 (en) 1996-01-10 2001-03-27 Aeroquip-Vickers International Gmbh Low-loss drive system for a plurality of hydraulic actuators

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ATE521813T1 (de) 2011-09-15
EP1911979A1 (de) 2008-04-16
DK1911979T3 (da) 2011-10-10
SI1911979T1 (sl) 2011-12-30

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