EP3045723B1 - Axial piston pump - Google Patents

Axial piston pump Download PDF

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Publication number
EP3045723B1
EP3045723B1 EP15151407.2A EP15151407A EP3045723B1 EP 3045723 B1 EP3045723 B1 EP 3045723B1 EP 15151407 A EP15151407 A EP 15151407A EP 3045723 B1 EP3045723 B1 EP 3045723B1
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EP
European Patent Office
Prior art keywords
pressure
line
piston pump
axial piston
way valve
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EP15151407.2A
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German (de)
French (fr)
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EP3045723A1 (en
Inventor
Georg Jemüller
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Hawe Hydraulik SE
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Hawe Hydraulik SE
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Priority to EP15151407.2A priority Critical patent/EP3045723B1/en
Publication of EP3045723A1 publication Critical patent/EP3045723A1/en
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Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04BPOSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/002Hydraulic systems to change the pump delivery
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03CPOSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
    • F03C1/00Reciprocating-piston liquid engines
    • F03C1/02Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders
    • F03C1/06Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinder axes generally coaxial with, or parallel or inclined to, main shaft axis
    • F03C1/0678Control
    • F03C1/0686Control by changing the inclination of the swash plate
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04BPOSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/26Control
    • F04B1/28Control of machines or pumps with stationary cylinders
    • F04B1/29Control of machines or pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
    • F04B1/295Control of machines or pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block by changing the inclination of the swash plate
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04BPOSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/26Control
    • F04B1/30Control of machines or pumps with rotary cylinder blocks
    • F04B1/32Control of machines or pumps with rotary cylinder blocks by varying the relative positions of a swash plate and a cylinder block
    • F04B1/324Control of machines or pumps with rotary cylinder blocks by varying the relative positions of a swash plate and a cylinder block by changing the inclination of the swash plate
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04BPOSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/08Regulating by delivery pressure

Definitions

  • the invention relates to an axial piston pump specified in the preamble of claim 1. Art.
  • known axial piston pump either with a control device with the license plate LP or the license plate LLSP (with a loadensing or Load pressure signal port) known axial piston pump is the multi-way valve in the second controller a spring-loaded pressure relief valve, which is arranged between the main line and the tank line and is mechanically adjusted by the angle lever against the spring force.
  • the main stage is operated exclusively with a pressure pilot control from the main line and is designed for example as a 3/3-way slide valve.
  • the first controller may be associated with a proportional pressure relief valve.
  • EP0939225 A2 is a common power control device for two or more parallel connected to each own main lines variable displacement known.
  • the common control device power regulator
  • an angle lever actuates a solenoid-operated multi-way valve.
  • the angle lever is acted upon in a pivoting direction about a fixed axis by an adjustable spring, and against the spring on a second arm via a sensing piston which is displaced along the arm against spring force tapped off from one main line control pressure.
  • the invention has for its object to provide an axial piston pump of the type mentioned, with the unwanted volume losses largely avoided, reduces the mechanical load on the hydraulic medium, and the efficiency can be increased.
  • the multi-way valve is brought directly from the angle lever in a switching position, in which from the reduced pressure of the pressure reducing valve, the main stage is adjusted so that the other actuating piston surface immediately sets the axial piston in the direction of zero promotion, if no load is to be moved, or in the case of a load to be moved, the axial piston pump resets so quickly that no appreciable volume losses occur.
  • the pressure reducing valve offers the advantage of applying to a relatively small constant reduced pressure of, for example, only 30 bar, the multi-way valve, which is thus small-scale and inexpensive.
  • the main stage has parallel to the pressure feedforward control from the main line to a pressurized with the Regelvor Taverndruck control pressure pilot control.
  • the Regelvor Taverntik is generated at the control pressure pilot control of the multi-way valve depending on the mechanical actuation by the angle lever from the reduced pressure of the pressure reducing valve, which needs to be, for example, at a maximum delivery pressure between 250 and 350 bar only mentioned 30 bar.
  • the control pilot pressure together with the control pressure at the pressure precontrol tapped from the main line, adjusts the main stage, e.g. to guide hydraulic medium with low throttling to the other actuating piston surface. Thanks to the pressure reducing valve results in a precisely predictable, sensitive control behavior, with only a small amount of control of the hydraulic medium to be moved at low pressures in a main part of the hydraulic circuit. Significant advantages are besides the exactly predictable control behavior an improved efficiency and a low mechanical load of the hydraulic medium.
  • a tank line is connected at least to the multi-way valve and the main stage in order to be able to relieve it when needed.
  • the one actuating piston surface is acted upon from the main line with the delivery pressure, for example, to adjust the axial piston pump in the direction of the maximum delivery volume, possibly combined with a spring.
  • the other actuating piston surface can be pressurized or relieved of pressure via the main stage, with the pressurization of the other actuating piston surface, for example, adjusting the axial piston pump in the direction of zero delivery or minimum delivery.
  • the main stage is a 3/2-way valve or a 4/2-way valve or a 3/3-way valve, preferably in slide construction, wherein the 3/3 - way valve may have a locked middle position, and is the Mehrfach- Directional valve a 3/2-way valve either in poppet or seat valve design.
  • the main stage of the first spring force can be acted upon to a switching position in which the other actuating piston surface is relieved to the tank line, however, the MehrWegeventil acted upon by the second spring force to a switching position in which the control pressure pilot control of the main stage connected to the tank line is.
  • the other actuating piston surface is the larger of the two, and this is arranged so that the axial piston pump is adjusted by her in the direction of zero promotion or minimum funding.
  • the pressure control for the delivery pressure has a significantly smaller first application area than a second, significantly larger admission area rule-pressure pilot control.
  • the first loading surface on which the delivery pressure from the main line acts, may be arranged on a pin connected to a valve element, while the second, larger admission surface for the crizvor suittik can be arranged in a much larger annular chamber on a circular surface of the valve element.
  • a connection with the tank line is made between the main stage and the other actuating piston surface in a connecting line, which is secured by a throttle.
  • the L regulator downstream of the pressure reducing valve is a proportional pressure relief valve, preferably a 3/2 Directional control valve, assigned.
  • an input port of the proportional pressure relief valve with the output of the pressure reducing valve an output port of the proportional pressure relief valve via a throttle with the spring side of MehrWegeventils and or via another throttle with an auxiliary piston surface for loading the angle lever against the second spring force, and a second port of the proportional pressure relief valve connected to the tank line.
  • certain throttles are then closed and others activated.
  • a 3/2-way valve is assigned to a LS function of the main stage in the N-controller, the first port to the main line, the second port to the tank line, and the third port to the line to the other actuating piston surface are connected ,
  • This 3/2-way valve is acted upon by a spring to a switching position in which the first connection is shut off and the second and third connections are connected.
  • the 3/2-way valve also has a spring-side pressure pilot control, which is connected to a LS port of the L-controller, and a spring side opposite pressure pilot control, which is connected to the main line. In this way, in the controller in the control and a load pressure signal is processed accordingly.
  • one arm of the bellcrank rests on the abutment which is movable with the other control piston surface, the pressure piston acting under the pressure in the main conduit on the opposite side of the arm of the bellcrank, in order to generate a moment with which the multi-way valve is actuated. wherein the moment changes depending on the delivery pressure and depending on the geometrical delivery volume corresponding position of the abutment along the arm of the angle lever.
  • the structural complexity of the L-regulator can be reduced if the sensing piston is integrated directly into the abutment, which moves with the other actuating piston surface, wherein the sensing piston receives the delivery pressure through the other actuating piston surface and, for example, a role of the abutment with a force presses against the angle lever, which depends on the delivery pressure.
  • the abutment fulfills a dual function here, as it returns the geometric delivery volume and the current delivery pressure in the scheme.
  • An axial piston pump 1 as an example of a variable displacement pump is in Fig. 1 equipped with a controller, which is made up of an L-controller L and an N-controller N (highlighted with dot-dash lines).
  • the axial piston pump 1 has a symbolically indicated pivoting cradle which is adjustable, for example by means of two adjusting pistons, namely an actuating piston with an actuating piston surface 3 and an actuating piston with an actuating piston surface 6, each in a control chamber 4, 7, to the axial pump between maximum promotion (in the drawing in Fig. 1 indicated) and zero promotion or minimum funding (not shown) to adjust.
  • One actuating piston surface 3 is smaller than the other actuating piston surface 6.
  • a spring 5 acts on the actuating piston surface 3 in order to set and maintain the axial piston pump 1 in a pressureless state for maximum delivery.
  • the delivery side is indicated by 8 '.
  • a main line 8 is connected, which possibly leads to an adjustable hydraulic load HL and components of the controller.
  • a tank line 9 is present.
  • an angle lever 10 is pivotally supported in a pivot bearing 11, wherein the pivot bearing 11 in the embodiment shown in FIG Fig. 1 in the direction of the vertical leg of the angle lever 10 is adjustable.
  • an abutment 11 On the horizontal leg of the angle lever 10 engages an abutment 11 which is movable with the actuating piston surface 6 having the adjusting piston and, so to speak, the geometric displacement returns.
  • a roller 12 At the abutment 11, a roller 12 may be arranged.
  • a Tastkolben 13 engages, which is acted upon from the main line 8 with the delivery pressure and generates a moment that adjusts a multi-way valve 14 between switch positions via a plunger 16.
  • the multi-way valve 14 is designed as a 3/2 way valve and is acted upon by a second spring force 15 against the angle lever 10.
  • the second spring force 15 tends to set the multi-way valve 14 in a switching position in which a line 19 is connected to the tank line 9 (as shown), and a connection of a line 18 is shut off.
  • the L regulator L is assigned a pressure-reducing valve 17 (or integrated therein), which is connected to the main line 8 and adjusts a reduced pressure in the line 18 to the multi-way valve 14, for example, about 30 bar.
  • the pressure reducing valve 17 may be connected to the tank line 9. (Leakage)
  • the N-controller N includes a multi-way multi-stage main stage 22, which in Fig. 1 is designed as a 3/3-way slide valve and connected to the main line 8 pressure precontrol 23 and parallel to a control pressure pilot 21, which act opposite to a first spring force 24 on a non-highlighted valve element.
  • the line 19 from the multi-way valve 14 is connected to the control pressure pilot 21 and includes, for example, a throttle 20.
  • the pilot control 23, which is connected to the main line 8, has a smaller loading area than the control pressure pilot 21.
  • the urging surface of the pressure pilot 23 is provided on a pin connected to the valve element, while the urging surface of the control pressure pilot 21 may be an annular surface in an annular chamber in the valve element (not shown).
  • a connection of the main stage 22 is connected to the main line 8, another, however, via a throttle 31 with the tank line 9. Further leads from another terminal of the main stage 22, a line 25 to the control chamber 7 of the other actuating piston surface 6.
  • This line 25 is connected via a Throttle 26 connected to the tank line 9.
  • a line 27 branches off via a throttle 28, for example, to a spring chamber of the first spring force 24 and further from this to the tank line 9, optionally via a throttle 29. Downstream of the throttle 29, an LS port 30 is indicated. If the LS connection 30 is used, the branch of the tank line 9 is removed there.
  • the axial piston pump 1 If the axial piston pump 1 starts, it is set to maximum delivery volume. If no hydraulic load HL is to be supplied, pressure builds up in the main line 8, which immediately pivots the angle lever via the sensing piston 13 and adjusts the multi-way valve 14. From the pressure in the main line 8, the pressure reducing valve 17 in the line 18 generates a reduced pressure from which the displaced multi-way valve 14 Regelvor askbuch for the Cannabisvor facedung 21 generates, so that by the pressure in the main line to the pilot control 23 and the Regelvor ask Kunststoff the Main stage 22 is adjusted and generates pressure in the previously relieved line 25 to the actuating piston surface 6, whereby the axial piston pump 1 is immediately adjusted in the direction of zero promotion.
  • the pressure in the main line 8 drops and is reduced via the pressure reducing valve 17 without significant throttling. If, on the other hand, a hydraulic load HL is to be supplied, then a balance is established between the moment of the angle lever 10 and the second spring force 5 and also between the forces from the pressure feedforward controls 23, 21 and the first spring force 24. If the axial piston pump 1 is stopped again, the line 19 is relieved to the tank line 9 and is relieved to the line 25 via the main stage to the tank line 9.
  • Fig. 2 shown embodiment of the axial piston pump differs from the in Fig. 1 essentially by two details.
  • the sensing piston 13 is integrated here in the abutment 11 and acts on the roller 12 on the horizontal leg of the angle lever 10 on the same side of the horizontal leg as the abutment 11, which moves with the actuating piston surface 3.
  • the sensing piston 13 is here pressurized from the main line 8 and the control chamber 4 of the actuating piston surface 3.
  • the main stage 22 ' is in this embodiment, a 3/2-way valve, for example in slide construction.
  • the main stage 22 ' is assigned a 3/2-way valve 31 whose one connection to the main line 8, the adjacent connection via the main stage 22' to the tank line 9, and a third connection with the line 25 to the other actuating piston surface 6 and via the throttle 26 are also connected to the tank line 9.
  • the 3/2-way valve 31 has on a pilot side 34 a connection from which a line 35 leads to the LS port 30, via a throttle 29, and also via a throttle 31 to the tank line 9.
  • the pilot side 34 is on the Side of a spring 32, the 3/2-way valve 31 in the in Fig. 2 shown switching position brings.
  • An opposite pilot control port 33 is connected to the main line 8.
  • the function of the regulator is similar to that of the regulator of Fig. 1 , in which case additionally the 3/2-way valve 31 for the application of the other actuating piston surface 6 can process a load pressure signal.
  • FIG. Fig. 3 which is essentially the embodiment of the Fig. 2 corresponds, an additional electric power adjustment is provided, wherein the power adjustment works either with a pressure increase or a pressure reduction of the control pilot pressure generated in the line 19.
  • a proportional pressure relief valve 36 with a proportional magnet 37 is provided in the L-controller L, which acts against a control spring 38.
  • the proportional pressure relief valve 36 is designed here as a 3/2 -Wededruckregelventil and arranged downstream of the pressure reducing valve 17.
  • An outlet port of the proportional pressure relief valve 36 is connected to the tank line 9, a second port to a branch line 18 'of the line 18 from the pressure reducing valve 17, and a third port to a line 39 which branches off into a line 40, on the one hand to an auxiliary piston 39, which engages opposite to the multi-way valve 14 on the vertical leg of the angle lever 10 and is connected via a throttle 42 to the tank line 9, and on the other hand to a spring chamber of the second spring force 15.
  • the spring chamber is also connected via a throttle 44 to the tank line 9. On both sides of the branch from the line 39 into the line 40 throttles 42, 41 are placed.
  • the throttle 41 is shut off, as well as the throttle 43, and the throttles 42 and 44 are active.
  • the structure in FIG Fig. 4 neither an electric power concept is provided, nor a processing of a load pressure signal. Except for the main stage 22 ", the structure largely corresponds to that of Fig. 2 , In contrast to Fig. 2 However, the main stage is 22 "designed as a 3/2-way valve, for example in spool design with the two pressure pilot controls 21, 23, and the line 25 is connected directly to the third terminal, so that the N-controller N only in accordance with between the forces in the pressure pilot controls 21, 23 and the first spring force 24, the admission of the other actuating piston surface 6 from the pressure in the main line 9 controls.
  • the feeler piston 13 is integrated into the abutment 11 to act on its role 12, and the probe piston from the chamber 4 is acted upon by the pressure in the main line 8.
  • the multi-way valve 14 since the multi-way valve 14 only needs to cope with the reduced pressure, it can be made small and inexpensive, and also the second spring force 15 is moderate. This also applies to the electric power concept in Fig. 3 in which the proportional pressure relief valve 36 is included only in a control line circuit that results in reduced pressure.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Control Of Positive-Displacement Pumps (AREA)
  • Fluid-Pressure Circuits (AREA)

Description

Die Erfindung betrifft eine Axialkolbenpumpe, der im Oberbegriff des Patentanspruchs 1 angegebenen Art.The invention relates to an axial piston pump specified in the preamble of claim 1. Art.

Bei der aus der Druckschrift D 7960 E-V 30E mit einem Druckdatum 07-2013, der Firma HAWE Hydraulik SE, 81608 München, Seite 9, unten, bekannten Axialkolbenpumpe, entweder mit einer Regelvorrichtung mit dem Kennzeichen LP oder dem Kennzeichen LLSP (mit einem loadsensing oder Lastdrucksignal-Anschluss) bekannten Axialkolbenpumpe ist das Mehr-Wegeventil im zweiten Regler ein federbeaufschlagtes Druckbegrenzungsventil, das zwischen der Hauptleitung und der Tankleitung angeordnet ist und durch den Winkelhebel mechanisch gegen die Federkraft verstellt wird. Die Hauptstufe wird ausschließlich mit einer Druckvorsteuerung aus der Hauptleitung betrieben und ist beispielsweise als 3/3-Wege-Schieberventil ausgebildet. Zur elektrischen Leistungsverstellung kann dem ersten Regler ein Proportional-Druckbegrenzungsventil zugeordnet sein. Da die Axialkolbenpumpe wie üblich mit maximalen Fördervolumen anläuft, entstehen unvermeidbar Betriebssituationen, bei denen ein Teil des geförderten Druckmittels über das noch nicht oder nur wenig vom Winkelhebel betätigte Druckbegrenzungsventil zur Tankleitung abströmt. Dies bedeutet erhebliches Verlustvolumen, und wegen starker Drosselverluste eine unerwünschte Erwärmung und hohe mechanische Belastung des Hydraulikmediums, und von Dichtungen im Hydraulikkreis. Außerdem verschlechtert das Verlustvolumen den Gesamtwirkungsgrad. Da das Druckbegrenzungsventil auch mit dem maximalen Fördervolumen und dem maximalen Druck zurechtkommen muss, ist es baulich aufwendig und teuer.In the known from the publication D 7960 EV 30E with a print date 07-2013, HAWE Hydraulik SE, 81608 Munich, page 9, bottom, known axial piston pump, either with a control device with the license plate LP or the license plate LLSP (with a loadensing or Load pressure signal port) known axial piston pump is the multi-way valve in the second controller a spring-loaded pressure relief valve, which is arranged between the main line and the tank line and is mechanically adjusted by the angle lever against the spring force. The main stage is operated exclusively with a pressure pilot control from the main line and is designed for example as a 3/3-way slide valve. For electrical power adjustment, the first controller may be associated with a proportional pressure relief valve. Since the axial piston pump starts as usual with maximum delivery volume, inevitably arise operating situations in which a portion of the conveyed pressure fluid flows through the not yet or only slightly actuated by the angle lever pressure relief valve to the tank line. This means considerable loss volume, and because of high throttle losses undesirable heating and high mechanical load of the hydraulic medium, and seals in the hydraulic circuit. In addition, the loss volume deteriorates the overall efficiency. Since the pressure relief valve also has to cope with the maximum delivery volume and the maximum pressure, it is structurally complex and expensive.

Aus DE3742111 A1 ist es bekannt, zwei Verstellpumpen jeweils mit einer eigenen Regelvorrichtung parallel an die Hauptleitung anzuschließen. Beide Regelvorrichtungen sind mit einer Rücklaufleitung verbunden, in der ein einstellbares Druckbegrenzungsventil enthalten ist, das in Aufsteuerrichtung gegen eine einstellbare Feder mit Steuerdruck aus der Hauptleitung gesteuert wird.Out DE3742111 A1 It is known to connect two variable displacement pumps each with its own control device in parallel to the main line. Both control devices are connected to a return line, in which an adjustable pressure relief valve is included, which is controlled in the up direction against an adjustable spring with control pressure from the main line.

Aus EP0939225 A2 ist eine gemeinsame Leistungsregeleinrichtung für zwei oder mehrere parallel an jeweils eigene Hauptleitungen angeschlossene Verstellpumpen bekannt. In der gemeinsamen Regelvorrichtung (Leistungsregler) betätigt ein Winkelhebel ein magnetbetätigtes Mehr-Wegeventil. Der Winkelhebel wird in einer Schwenkrichtung um eine feststehende Achse durch eine einstellbare Feder beaufschlagt, und gegen die Feder an einem zweiten Arm über einen Tastkolben, der entlang des Arms gegen Federkraft mit aus jeweils einer Hauptleitung abgegriffenem Steuerdruck verschoben wird.Out EP0939225 A2 is a common power control device for two or more parallel connected to each own main lines variable displacement known. In the common control device (power regulator) an angle lever actuates a solenoid-operated multi-way valve. The angle lever is acted upon in a pivoting direction about a fixed axis by an adjustable spring, and against the spring on a second arm via a sensing piston which is displaced along the arm against spring force tapped off from one main line control pressure.

Der Erfindung liegt die Aufgabe zugrunde, eine Axialkolbenpumpe der eingangs genannten Art anzugeben, mit der unerwünschte Volumenverluste weitestgehend vermieden, die mechanische Belastung des Hydraulikmediums verringert, und der Wirkungsgrad gesteigert werden.The invention has for its object to provide an axial piston pump of the type mentioned, with the unwanted volume losses largely avoided, reduces the mechanical load on the hydraulic medium, and the efficiency can be increased.

Die gestellte Aufgabe wird mit den Merkmalen des Patentanspruches 1 gelöst.The stated object is achieved with the features of claim 1.

Selbst wenn die Axialkolbenpumpe mit maximalem Fördervolumen anläuft, wird das Mehr-Wegeventil vom Winkelhebel unmittelbar in eine Schaltstellung gebracht, in der aus dem geminderten Druck des Druckminderventils die Hauptstufe so verstellt wird, dass die andere Stellkolbenfläche die Axialkolbenpumpe umgehend in Richtung zur Nullförderung stellt, sofern keine Last zu bewegen ist, bzw. im Falle einer zu bewegenden Last die Axialkolbenpumpe so rasch zurückstellt, dass keine nennenswerten Volumenverluste auftreten. Ferner bietet das Druckminderventil den Vorteil, mit einem relativ geringen konstanten geminderten Druck von beispielsweise nur 30 bar das Mehr-Wegeventil zu beaufschlagen, das somit kleinbauend und kostengünstig ist. Die Hauptstufe weist parallel zur Druckvorsteuerung aus der Hauptleitung eine mit dem Regelvorsteuerdruck beaufschlagbare Regel-Druckvorsteuerung auf. Der Regelvorsteuerdruck wird an der Regel-Druckvorsteuerung vom Mehr-Wegeventil abhängig von der mechanischen Betätigung durch den Winkelhebel aus dem geminderten Druck des Druckminderventils erzeugt, der beispielsweise bei einem maximalen Förderdruck zwischen 250 und 350 bar nur die erwähnten 30 bar zu betragen braucht. Der Regelvorsteuerdruck verstellt zusammen mit dem aus der Hauptleitung abgegriffenen Steuerdruck an der Druckvorsteuerung die Hauptstufe z.B. um Hydraulikmedium mit geringer Drosselung zur anderen Stellkolbenfläche zu führen. Dank des Druckminderventils ergibt sich ein exakt vorherbestimmbares, feinfühliges Regelverhalten, wobei in einem Hauptteil der Hydraulikschaltung nur geringe Steuermengen des Hydraulikmediums bei geringen Drücken zu bewegen sind. Wesentliche Vorteile sind neben dem exakt vorherbestimmbaren Regelverhalten ein verbesserter Wirkungsgrad und eine geringe mechanische Belastung des Hydraulikmediums.Even if the axial piston pump starts with maximum delivery volume, the multi-way valve is brought directly from the angle lever in a switching position, in which from the reduced pressure of the pressure reducing valve, the main stage is adjusted so that the other actuating piston surface immediately sets the axial piston in the direction of zero promotion, if no load is to be moved, or in the case of a load to be moved, the axial piston pump resets so quickly that no appreciable volume losses occur. Furthermore, the pressure reducing valve offers the advantage of applying to a relatively small constant reduced pressure of, for example, only 30 bar, the multi-way valve, which is thus small-scale and inexpensive. The main stage has parallel to the pressure feedforward control from the main line to a pressurized with the Regelvorsteuerdruck control pressure pilot control. The Regelvorsteuerdruck is generated at the control pressure pilot control of the multi-way valve depending on the mechanical actuation by the angle lever from the reduced pressure of the pressure reducing valve, which needs to be, for example, at a maximum delivery pressure between 250 and 350 bar only mentioned 30 bar. The control pilot pressure, together with the control pressure at the pressure precontrol tapped from the main line, adjusts the main stage, e.g. to guide hydraulic medium with low throttling to the other actuating piston surface. Thanks to the pressure reducing valve results in a precisely predictable, sensitive control behavior, with only a small amount of control of the hydraulic medium to be moved at low pressures in a main part of the hydraulic circuit. Significant advantages are besides the exactly predictable control behavior an improved efficiency and a low mechanical load of the hydraulic medium.

Bei einer zweckmäßigen Ausführungsform ist eine Tankleitung zumindest an das MehrWegeventil und die Hauptstufe angeschlossen, um diese bei Bedarf entlasten zu können. Die eine Stellkolbenfläche wird aus der Hauptleitung mit dem Förderdruck beaufschlagt, beispielsweise um die Axialkolbenpumpe in Richtung zum maximalen Fördervolumen zu verstellen, ggf. kombiniert mit einer Feder. Hingegen ist die andere Stellkolbenfläche über die Hauptstufe druckbeaufschlagbar oder druckentlastbar, wobei die Druckbeaufschlagung der anderen Stellkolbenfläche beispielsweise die Axialkolbenpumpe in Richtung zur Nullförderung oder Minimalförderung verstellt.In an expedient embodiment, a tank line is connected at least to the multi-way valve and the main stage in order to be able to relieve it when needed. The one actuating piston surface is acted upon from the main line with the delivery pressure, for example, to adjust the axial piston pump in the direction of the maximum delivery volume, possibly combined with a spring. By contrast, the other actuating piston surface can be pressurized or relieved of pressure via the main stage, with the pressurization of the other actuating piston surface, for example, adjusting the axial piston pump in the direction of zero delivery or minimum delivery.

Bei einer zweckmäßigen Ausführungsform ist die Hauptstufe ein 3/2-Wegeventil oder ein 4/2-Wegeventil oder ein 3/3-Wegeventil, vorzugsweise in Schieberbauweise, wobei das 3/3 - Wegeventil eine abgesperrte Mittelstellung aufweisen kann, und ist das Mehr-Wegeventil ein 3/2-Wegeventil entweder in Schieber- oder in Sitzventilbauweise. Hierbei ist, vorzugsweise, die Hauptstufe von der ersten Federkraft zu einer Schaltstellung beaufschlagbar, in der die andere Stellkolbenfläche zur Tankleitung entlastet ist, hingegen das MehrWegeventil von der zweiten Federkraft zu einer Schaltstellung beaufschlagbar, in der die Regel-Druckvorsteuerung der Hauptstufe mit der Tankleitung verbunden ist.In an expedient embodiment, the main stage is a 3/2-way valve or a 4/2-way valve or a 3/3-way valve, preferably in slide construction, wherein the 3/3 - way valve may have a locked middle position, and is the Mehrfach- Directional valve a 3/2-way valve either in poppet or seat valve design. In this case, preferably, the main stage of the first spring force can be acted upon to a switching position in which the other actuating piston surface is relieved to the tank line, however, the MehrWegeventil acted upon by the second spring force to a switching position in which the control pressure pilot control of the main stage connected to the tank line is.

Bei einer zweckmäßigen Ausführungsform ist die andere Stellkolbenfläche die größere der beiden, und ist diese so angeordnet, dass von ihr die Axialkolbenpumpe in Richtung zur Nullförderung oder Minimalförderung verstellt wird.In an advantageous embodiment, the other actuating piston surface is the larger of the two, and this is arranged so that the axial piston pump is adjusted by her in the direction of zero promotion or minimum funding.

Im Hinblick darauf, dass der Förderdruck in der Hauptleitung wesentlich höher ist als der geminderte Druck oder der Regel-Vorsteuerdruck, ist es wichtig, dass in der Hauptstufe die Drucksteuerung für den Förderdruck eine erheblich kleinere erste Beaufschlagungsfläche aufweist als eine zweite, deutlich größere Beaufschlagungsfläche der Regel-Druckvorsteuerung.In view of the fact that the delivery pressure in the main line is substantially higher than the reduced pressure or the control pilot pressure, it is important that in the main stage, the pressure control for the delivery pressure has a significantly smaller first application area than a second, significantly larger admission area rule-pressure pilot control.

Konkret kann die erste Beaufschlagungsfläche, auf der der Förderdruck aus der Hauptleitung wirkt, an einem mit einem Ventilelement verbundenen Stift angeordnet sein, während die zweite, größere Beaufschlagungsfläche für den Regelvorsteuerdruck in einer deutlich größeren Ringkammer auf einer Kreisringfläche des Ventilelements angeordnet sein kann.Concretely, the first loading surface, on which the delivery pressure from the main line acts, may be arranged on a pin connected to a valve element, while the second, larger admission surface for the Regelvorsteuerdruck can be arranged in a much larger annular chamber on a circular surface of the valve element.

Um sicherzustellen, dass die andere Stellkolbenfläche keine ungewollte Verstellung der Axialkolbenpumpe vornimmt, wenn dies vom Regler nicht eingesteuert ist, wird zwischen der Hauptstufe und der anderen Stellkolbenfläche in einer diese verbindenden Leitung eine Verbindung mit der Tankleitung hergestellt, die durch eine Drossel abgesichert ist.To ensure that the other actuating piston surface does not make an unintentional adjustment of the axial piston pump, if this is not controlled by the controller, a connection with the tank line is made between the main stage and the other actuating piston surface in a connecting line, which is secured by a throttle.

Um eine elektrische Leistungsverstellung vornehmen zu können, ist bei einer zweckmäßigen Ausführungsform zur Druckanhebung oder Druckabsenkung des der Regel-Druckvorsteuerung der Hauptstufe gelieferten Regel-Vorsteuerdrucks aus dem geminderten Druck dem L-Regler stromab des Druckminderventils ein Proportional-Druckbegrenzungsventil, vorzugsweise ein 3/2-Wegeventil, zugeordnet.In order to be able to carry out an electrical power adjustment, in the case of an expedient embodiment for increasing or decreasing the pressure of the regulated pressure control of the main stage from the reduced pressure, the L regulator downstream of the pressure reducing valve is a proportional pressure relief valve, preferably a 3/2 Directional control valve, assigned.

Um von vornherein beide Möglichkeiten, d.h. entweder eine Druckanhebung oder eine Druckabsenkung elektrisch einsteuern zu können, ist bei einer zweckmäßigen Ausführungsform ein Eingangsanschluss des Proportional-Druckbegrenzungsventils mit dem Ausgang des Druckminderventils, ein Ausgangsanschluss des Proportional-Druckbegrenzungsventils über eine Drossel mit der Federseite des MehrWegeventils und/oder über eine andere Drossel mit einer Hilfskolbenfläche zum Belasten des Winkelhebels gegen die zweite Federkraft, und ein zweiter Anschluss des Proportional-Druckbegrenzungsventils mit der Tankleitung verbunden. Je nachdem, ob eine Druckanhebung oder eine Druckabsenkung elektrisch gesteuert werden soll, werden dann bestimmte Drosseln verschlossen und andere aktiviert.To be able to control from the outset both options, ie either a pressure increase or a pressure reduction, is in an advantageous embodiment, an input port of the proportional pressure relief valve with the output of the pressure reducing valve, an output port of the proportional pressure relief valve via a throttle with the spring side of MehrWegeventils and or via another throttle with an auxiliary piston surface for loading the angle lever against the second spring force, and a second port of the proportional pressure relief valve connected to the tank line. Depending on whether a pressure increase or a pressure reduction is to be controlled electrically, certain throttles are then closed and others activated.

Bei einer weiteren Ausführungsform ist für eine LS-Funktion der Hauptstufe im N-Regler ein 3/2-Wegeventil zugeordnet, dessen erster Anschluss an die Hauptleitung, dessen zweiter Anschluss an die Tankleitung, und dessen dritter Anschluss an die Leitung zur anderen Stellkolbenfläche angeschlossen sind. Dieses 3/2-Wegeventil wird durch eine Feder zu einer Schaltstellung beaufschlagt, in der der erste Anschluss abgesperrt und die zweiten und dritten Anschlüsse verbunden sind. Das 3/2-Wegeventil weist ferner eine federseitige Druckvorsteuerung auf, die mit einem LS-Anschluss des L-Reglers verbunden ist, sowie eine der Federseite entgegengesetzte Druckvorsteuerung, die an die Hauptleitung angeschlossen ist. Auf diese Weise wird im Regler bei der Regelung auch ein Lastdrucksignal entsprechend verarbeitbar.In a further embodiment, a 3/2-way valve is assigned to a LS function of the main stage in the N-controller, the first port to the main line, the second port to the tank line, and the third port to the line to the other actuating piston surface are connected , This 3/2-way valve is acted upon by a spring to a switching position in which the first connection is shut off and the second and third connections are connected. The 3/2-way valve also has a spring-side pressure pilot control, which is connected to a LS port of the L-controller, and a spring side opposite pressure pilot control, which is connected to the main line. In this way, in the controller in the control and a load pressure signal is processed accordingly.

Konventionell liegt ein Arm des Winkelhebels auf dem mit der anderen Stellkolbenfläche bewegbaren Widerlager auf, wobei der Tastkolben unter dem Druck in der Hauptleitung auf der entgegengesetzten Seite des Arms des Winkelhebels einwirkt, um ein Moment zu erzeugen, mit dem das Mehrwege-Ventil betätigt wird, wobei sich das Moment abhängig vom Förderdruck und abhängig von der dem geometrischen Fördervolumen entsprechenden Position des Widerlagers entlang des Arms des Winkelhebels ändert. Der bauliche Aufwand des L-Reglers lässt sich jedoch dadurch vermindern, wenn der Tastkolben gleich in das Widerlager integriert wird, das mit der anderen Stellkolbenfläche mitfährt, wobei der Tastkolben den Förderdruck durch die andere Stellkolbenfläche hindurch aufnimmt und beispielsweise eine Rolle des Widerlagers mit einer Kraft gegen den Winkelhebel drückt, die vom Förderdruck abhängt. Das Widerlager erfüllt hier eine zweifache Funktion, da es das geometrische Fördervolumen und den aktuellen Förderdruck in die Regelung rückführt.Conventionally, one arm of the bellcrank rests on the abutment which is movable with the other control piston surface, the pressure piston acting under the pressure in the main conduit on the opposite side of the arm of the bellcrank, in order to generate a moment with which the multi-way valve is actuated. wherein the moment changes depending on the delivery pressure and depending on the geometrical delivery volume corresponding position of the abutment along the arm of the angle lever. However, the structural complexity of the L-regulator can be reduced if the sensing piston is integrated directly into the abutment, which moves with the other actuating piston surface, wherein the sensing piston receives the delivery pressure through the other actuating piston surface and, for example, a role of the abutment with a force presses against the angle lever, which depends on the delivery pressure. The abutment fulfills a dual function here, as it returns the geometric delivery volume and the current delivery pressure in the scheme.

Ausführungsformen des Erfindungsgegenstands werden anhand der Zeichnung erläutert. Es zeigen:

  • Fig. 1 ein Blockschaltbild einer ersten Ausführungsform einer Axialkolbenpumpe, wobei hier die wahlweise Möglichkeit der Nutzung eines LS-Anschlusses gegeben ist,
  • Fig. 2 ein Blockschaltbild einer weiteren Ausführungsform mit einer LS-Funktion,
  • Fig. 3 ein Blockschaltbild einer weiteren Ausführungsform, ähnlich der Form Fig. 2, ergänzt jedoch durch eine elektrische Leistungsverstellung in zwei Detailvarianten, und
  • Fig. 4 Blockschaltbild einer weiteren, einfachen Ausführungsform einer Axialkolbenpumpe mit einem mechanischen Regler.
Embodiments of the subject invention will be explained with reference to the drawing. Show it:
  • Fig. 1 FIG. 2 is a block diagram of a first embodiment of an axial piston pump, with the optional option of using an LS connection being given here.
  • Fig. 2 a block diagram of another embodiment with an LS function,
  • Fig. 3 a block diagram of another embodiment, similar to the form Fig. 2 , but supplemented by an electric power adjustment in two detail variants, and
  • Fig. 4 Block diagram of another simple embodiment of an axial piston pump with a mechanical regulator.

Eine Axialkolbenpumpe 1 als Beispiel einer Verstellpumpe ist in Fig. 1 mit einem Regler ausgestattet, der aus einem L-Regler L und einem N-Regler N erstellt ist (jeweils strichpunktiert hervorgehoben).An axial piston pump 1 as an example of a variable displacement pump is in Fig. 1 equipped with a controller, which is made up of an L-controller L and an N-controller N (highlighted with dot-dash lines).

Die Axialkolbenpumpe 1 weist eine symbolisch angedeutete Schwenkwiege auf, die beispielsweise mittels zweier Stellkolben, nämlich eines Stellkolbens mit einer Stellkolbenfläche 3 und eines Stellkolbens mit einer Stellkolbenfläche 6, jeweils in einer Steuerkammer 4, 7, verstellbar ist, um die Axialpumpe zwischen maximaler Förderung (in der Zeichnung in Fig. 1 angedeutet) und Nullförderung oder Minimalförderung (nicht gezeigt) zu verstellen. Die eine Stellkolbenfläche 3 ist kleiner als die andere Stellkolbenfläche 6. An der Stellkolbenfläche 3 greift beispielsweise eine Feder 5 an, um die Axialkolbenpumpe 1 in drucklosen Zustand zur Maximalförderung zu stellen und zu halten. Die Förderseite ist mit 8' angedeutet. Dort ist eine Hauptleitung 8 angeschlossen, die ggf. zu einer verstellbaren hydraulischen Last HL sowie zu Komponenten des Reglers führt. Ferner ist eine Tankleitung 9 vorhanden.The axial piston pump 1 has a symbolically indicated pivoting cradle which is adjustable, for example by means of two adjusting pistons, namely an actuating piston with an actuating piston surface 3 and an actuating piston with an actuating piston surface 6, each in a control chamber 4, 7, to the axial pump between maximum promotion (in the drawing in Fig. 1 indicated) and zero promotion or minimum funding (not shown) to adjust. One actuating piston surface 3 is smaller than the other actuating piston surface 6. For example, a spring 5 acts on the actuating piston surface 3 in order to set and maintain the axial piston pump 1 in a pressureless state for maximum delivery. The delivery side is indicated by 8 '. There, a main line 8 is connected, which possibly leads to an adjustable hydraulic load HL and components of the controller. Furthermore, a tank line 9 is present.

Im L-Regler L ist ein Winkelhebel 10 in einem Schwenklager 11 schwenkbar abgestützt, wobei das Schwenklager 11 bei der gezeigten Ausführungsform in Fig. 1 in Richtung des vertikalen Schenkels des Winkelhebels 10 verstellbar ist. Am horizontalen Schenkel des Winkelhebels 10 greift ein Widerlager 11 an, das mit dem die Stellkolbenfläche 6 aufweisenden Stellkolben verfahrbar ist und sozusagen das geometrische Fördervolumen rückführt. Am Widerlager 11 kann eine Rolle 12 angeordnet sein. An der anderen Seite des horizontalen Schenkels des Winkelhebels 10 greift ein Tastkolben 13 an, der aus der Hauptleitung 8 mit dem Förderdruck beaufschlagt wird und ein Moment erzeugt, das über einen Stössel 16 ein Mehr-Wegeventil 14 zwischen Schaltstellungen verstellt. Das Mehr-Wegeventil 14 ist als 3/2 -Wegeventil ausgebildet und wird durch eine zweite Federkraft 15 gegen den Winkelhebel 10 beaufschlagt. Die zweite Federkraft 15 ist bestrebt, das Mehr-Wegeventil 14 in eine Schaltstellung einzustellen, in der eine Leitung 19 mit der Tankleitung 9 verbunden ist (wie gezeigt), und ein Anschluss einer Leitung 18 abgesperrt ist.In the L-controller L, an angle lever 10 is pivotally supported in a pivot bearing 11, wherein the pivot bearing 11 in the embodiment shown in FIG Fig. 1 in the direction of the vertical leg of the angle lever 10 is adjustable. On the horizontal leg of the angle lever 10 engages an abutment 11 which is movable with the actuating piston surface 6 having the adjusting piston and, so to speak, the geometric displacement returns. At the abutment 11, a roller 12 may be arranged. On the other side of the horizontal leg of the angle lever 10, a Tastkolben 13 engages, which is acted upon from the main line 8 with the delivery pressure and generates a moment that adjusts a multi-way valve 14 between switch positions via a plunger 16. The multi-way valve 14 is designed as a 3/2 way valve and is acted upon by a second spring force 15 against the angle lever 10. The second spring force 15 tends to set the multi-way valve 14 in a switching position in which a line 19 is connected to the tank line 9 (as shown), and a connection of a line 18 is shut off.

Dem L-Regler L ist erfindungsgemäß ein Druckminderventil 17 zugeordnet (oder in diesen integriert), das an die Hauptleitung 8 angeschlossen ist und in der Leitung 18 zum Mehr-Wegeventil 14 einen geminderten Druck einstellt, beispielsweise etwas 30 bar. Das Druckminderventil 17 kann mit der Tankleitung 9 verbunden sein. (Leckage)According to the invention, the L regulator L is assigned a pressure-reducing valve 17 (or integrated therein), which is connected to the main line 8 and adjusts a reduced pressure in the line 18 to the multi-way valve 14, for example, about 30 bar. The pressure reducing valve 17 may be connected to the tank line 9. (Leakage)

Der N-Regler N enthält eine Mehr-Wege-Mehrstellungs-Hauptstufe 22, die in Fig. 1 als 3/3-Wege-Schieberventil ausgebildet ist und eine an die Hauptleitung 8 angeschlossene Druckvorsteuerung 23 sowie parallel dazu eine Regel-Druckvorsteuerung 21 aufweist, die entgegengesetzt zu einer ersten Federkraft 24 an einem nicht hervorgehobenen Ventilelement wirken. Die Leitung 19 vom Mehr-Wegeventil 14 ist an die Regel-Druckvorsteuerung 21 angeschlossen und enthält beispielsweise eine Drossel 20. Die Vorsteuerung 23, die an die Hauptleitung 8 angeschlossen ist, weist eine kleinere Beaufschlagungsfläche auf, als die Regel-Druckvorsteuerung 21. Beispielsweise ist die Beaufschlagungsfläche der Druckvorsteuerung 23 an einem mit dem Ventilelement verbundenen Stift vorgesehen, während die Beaufschlagungsfläche der Regel-Druckvorsteuerung 21 eine Kreisringfläche in einer Ringkammer beim Ventilelement sein kann (nicht gezeigt).The N-controller N includes a multi-way multi-stage main stage 22, which in Fig. 1 is designed as a 3/3-way slide valve and connected to the main line 8 pressure precontrol 23 and parallel to a control pressure pilot 21, which act opposite to a first spring force 24 on a non-highlighted valve element. The line 19 from the multi-way valve 14 is connected to the control pressure pilot 21 and includes, for example, a throttle 20. The pilot control 23, which is connected to the main line 8, has a smaller loading area than the control pressure pilot 21. For example the urging surface of the pressure pilot 23 is provided on a pin connected to the valve element, while the urging surface of the control pressure pilot 21 may be an annular surface in an annular chamber in the valve element (not shown).

Ein Anschluss der Hauptstufe 22 ist mit der Hauptleitung 8 verbunden, ein weiterer hingegen über eine Drossel 31 mit der Tankleitung 9. Ferner führt von einem weiteren Anschluss der Hauptstufe 22 eine Leitung 25 zur Steuerkammer 7 der anderen Stellkolbenfläche 6. Diese Leitung 25 ist über eine Drossel 26 mit der Tankleitung 9 verbunden. Von der Leitung 19 zweigt eine Leitung 27 über eine Drossel 28 beispielsweise zu einer Federkammer der ersten Federkraft 24 ab und weiter von dieser zur Tankleitung 9, gegebenenfalls über eine Drossel 29. Stromab der Drossel 29 ist ein LS-Anschluss 30 angedeutet. Wird der LS-Anschluss 30 benutzt, ist dort der Ast der Tankleitung 9 entfernt.A connection of the main stage 22 is connected to the main line 8, another, however, via a throttle 31 with the tank line 9. Further leads from another terminal of the main stage 22, a line 25 to the control chamber 7 of the other actuating piston surface 6. This line 25 is connected via a Throttle 26 connected to the tank line 9. From the line 19, a line 27 branches off via a throttle 28, for example, to a spring chamber of the first spring force 24 and further from this to the tank line 9, optionally via a throttle 29. Downstream of the throttle 29, an LS port 30 is indicated. If the LS connection 30 is used, the branch of the tank line 9 is removed there.

Funktion:Function:

Läuft die Axialkolbenpumpe 1 an, so ist sie auf maximales Fördervolumen eingestellt. Ist keine hydraulische Last HL zu versorgen, baut sich in der Hauptleitung 8 Druck auf, der umgehend über den Tastkolben 13 den Winkelhebel verschwenkt und das Mehr-Wegeventil 14 verstellt. Aus dem Druck in der Hauptleitung 8 erzeugt das Druckminderventil 17 in der Leitung 18 einen geminderten Druck, aus dem das verstellte Mehr-Wegeventil 14 Regelvorsteuerdruck für die Regelvorsteuerung 21 erzeugt, so dass durch den Druck in der Hauptleitung an der Vorsteuerung 23 und den Regelvorsteuerdruck die Hauptstufe 22 verstellt wird und Druck in die bis dahin entlastete Leitung 25 zur Stellkolbenfläche 6 erzeugt, wodurch die Axialkolbenpumpe 1 umgehend in Richtung zur Nullförderung verstellt wird. Der Druck in der Hauptleitung 8 sinkt und wird über das Druckminderventil 17 ohne nennenswerte Drosselung abgebaut. Ist hingegen eine hydraulische Last HL zu versorgen, dann stellt sich ein Gleichgewicht zwischen dem Moment des Winkelhebels 10 und der zweiten Federkraft 5 und auch zwischen den Kräften aus den Druckvorsteuerungen 23, 21 und der ersten Federkraft 24 ein. Wird die Axialkolbenpumpe 1 wieder stillgesetzt, wird die Leitung 19 zum Tankleitung 9 entlastet und wird auf die Leitung 25 über die Hauptstufe zur Tankleitung 9 entlastet.If the axial piston pump 1 starts, it is set to maximum delivery volume. If no hydraulic load HL is to be supplied, pressure builds up in the main line 8, which immediately pivots the angle lever via the sensing piston 13 and adjusts the multi-way valve 14. From the pressure in the main line 8, the pressure reducing valve 17 in the line 18 generates a reduced pressure from which the displaced multi-way valve 14 Regelvorsteuerdruck for the Regelvorsteuerung 21 generates, so that by the pressure in the main line to the pilot control 23 and the Regelvorsteuerdruck the Main stage 22 is adjusted and generates pressure in the previously relieved line 25 to the actuating piston surface 6, whereby the axial piston pump 1 is immediately adjusted in the direction of zero promotion. The pressure in the main line 8 drops and is reduced via the pressure reducing valve 17 without significant throttling. If, on the other hand, a hydraulic load HL is to be supplied, then a balance is established between the moment of the angle lever 10 and the second spring force 5 and also between the forces from the pressure feedforward controls 23, 21 and the first spring force 24. If the axial piston pump 1 is stopped again, the line 19 is relieved to the tank line 9 and is relieved to the line 25 via the main stage to the tank line 9.

Die in Fig. 2 gezeigte Ausführungsform der Axialkolbenpumpe unterscheidet sich von der in Fig. 1 im Wesentlichen durch zwei Details. Der Tastkolben 13 ist hier in das Widerlager 11 integriert und beaufschlagt die Rolle 12 am horizontalen Schenkel des Winkelhebels 10 auf der gleichen Seite des horizontalen Schenkels wie das Widerlager 11, das mit der Stellkolbenfläche 3 verfährt. Der Tastkolben 13 wird hier aus der Hauptleitung 8 und der Steuerkammer 4 der Stellkolbenfläche 3 mit Druck beaufschlagt.In the Fig. 2 shown embodiment of the axial piston pump differs from the in Fig. 1 essentially by two details. The sensing piston 13 is integrated here in the abutment 11 and acts on the roller 12 on the horizontal leg of the angle lever 10 on the same side of the horizontal leg as the abutment 11, which moves with the actuating piston surface 3. The sensing piston 13 is here pressurized from the main line 8 and the control chamber 4 of the actuating piston surface 3.

Die Hauptstufe 22' ist in dieser Ausführungsform ein 3/2-Wegeventil, beispielsweise in Schieberbauweise. Um bei der Regelung auch ein Lastdrucksignal am LS-Anschluss 30 zu verarbeiten, ist der Hauptstufe 22' ein 3/2-Wegeventil 31 zugeordnet, dessen einer Anschluss mit der Hauptleitung 8, der benachbarte Anschluss über die Hauptstufe 22' mit der Tankleitung 9, und ein dritter Anschluss mit der Leitung 25 zur anderen Stellkolbenfläche 6 und über die Drossel 26 auch mit der Tankleitung 9 verbunden sind. Das 3/2-Wegeventil 31 besitzt an einer Vorsteuerseite 34 einen Anschluss, von dem eine Leitung 35 zum LS-Anschluss 30 führt, und zwar über eine Drossel 29, und auch über eine Drossel 31 zur Tankleitung 9. Die Vorsteuerseite 34 ist auf der Seite einer Feder 32, die das 3/2-Wegeventil 31 in die in Fig. 2 gezeigte Schaltstellung bringt. Ein gegenüberliegender Vorsteueranschluss 33 ist hingegen mit der Hauptleitung 8 verbunden.The main stage 22 'is in this embodiment, a 3/2-way valve, for example in slide construction. In order to also process a load pressure signal at the LS connection 30 during the control, the main stage 22 'is assigned a 3/2-way valve 31 whose one connection to the main line 8, the adjacent connection via the main stage 22' to the tank line 9, and a third connection with the line 25 to the other actuating piston surface 6 and via the throttle 26 are also connected to the tank line 9. The 3/2-way valve 31 has on a pilot side 34 a connection from which a line 35 leads to the LS port 30, via a throttle 29, and also via a throttle 31 to the tank line 9. The pilot side 34 is on the Side of a spring 32, the 3/2-way valve 31 in the in Fig. 2 shown switching position brings. An opposite pilot control port 33, however, is connected to the main line 8.

Die Funktion des Reglers ist ähnlich der des Reglers von Fig. 1, wobei hier zusätzlich das 3/2-Wegeventil 31 für die Beaufschlagung der anderen Stellkolbenfläche 6 ein Lastdrucksignal verarbeiten kann.The function of the regulator is similar to that of the regulator of Fig. 1 , in which case additionally the 3/2-way valve 31 for the application of the other actuating piston surface 6 can process a load pressure signal.

In der Ausführungsform in Fig. 3, die im Wesentlichen der Ausführungsform der Fig. 2 entspricht, ist zusätzlich eine elektrische Leistungsverstellung vorgesehen, wobei die Leistungsverstellung entweder mit einer Druckanhebung oder einer Druckabsenkung des in der Leitung 19 erzeugten Regel-Vorsteuerdrucks arbeitet.In the embodiment in FIG Fig. 3 , which is essentially the embodiment of the Fig. 2 corresponds, an additional electric power adjustment is provided, wherein the power adjustment works either with a pressure increase or a pressure reduction of the control pilot pressure generated in the line 19.

In der gezeigten Ausführungsform ist im L-Regler L ein Proportional-Druckbegrenzungsventil 36 mit einem Proportional-Magneten 37 vorgesehen, der gegen eine Regelfeder 38 wirkt. Das Proportional-Druckbegrenzungsventil 36 ist hier als 3/2 -Wegedruckregelventil ausgebildet und stromab des Druckminderventils 17 angeordnet. Ein Auslassanschluss des Proportional-Druckbegrenzungsventils 36 ist an die Tankleitung 9, ein zweiter Anschluss an eine Zweigleitung 18' der Leitung 18 vom Druckminderventil 17, und ein dritter Anschluss an eine Leitung 39 angeschlossen, die sich in eine Leitung 40 aufzweigt, einerseits zu einem Hilfskolben 39, der gegenüberliegend zum Mehr-Wegeventil 14 am vertikalen Schenkel des Winkelhebels 10 angreift und über eine Drossel 42 mit der Tankleitung 9 verbunden ist, und andererseits zu einer Federkammer der zweiten Federkraft 15. Die Federkammer ist über eine Drossel 44 ebenfalls mit der Tankleitung 9 verbunden. Beiderseits der Abzweigung von der Leitung 39 in die Leitung 40 sind Drosseln 42, 41 platziert.In the embodiment shown, a proportional pressure relief valve 36 with a proportional magnet 37 is provided in the L-controller L, which acts against a control spring 38. The proportional pressure relief valve 36 is designed here as a 3/2 -Wededruckregelventil and arranged downstream of the pressure reducing valve 17. An outlet port of the proportional pressure relief valve 36 is connected to the tank line 9, a second port to a branch line 18 'of the line 18 from the pressure reducing valve 17, and a third port to a line 39 which branches off into a line 40, on the one hand to an auxiliary piston 39, which engages opposite to the multi-way valve 14 on the vertical leg of the angle lever 10 and is connected via a throttle 42 to the tank line 9, and on the other hand to a spring chamber of the second spring force 15. The spring chamber is also connected via a throttle 44 to the tank line 9. On both sides of the branch from the line 39 into the line 40 throttles 42, 41 are placed.

Je nachdem, ob eine Druckanhebung oder eine Druckabsenkung gewünscht wird, wird wie folgt vorgegangen:
Für eine Druckanhebung ist die Drossel 41 aktiv und werden die Drossel 42 wie auch die Drossel 44 versperrt. Die Drossel 43 ist aktiv.
Depending on whether a pressure increase or a pressure reduction is desired, proceed as follows:
For a pressure increase, the throttle 41 is active and the throttle 42 as well as the throttle 44 are blocked. The throttle 43 is active.

Wird hingegen eine Druckabsenkung gewünscht, ist die Drossel 41 abgesperrt, wie auch die Drossel 43, und sind die Drosseln 42 und 44 aktiv.However, if a pressure reduction is desired, the throttle 41 is shut off, as well as the throttle 43, and the throttles 42 and 44 are active.

Bei Bestromen des Proportional-Magneten 37 wird damit sozusagen der Widerstand der zweiten Federkraft 15 erhöht oder vermindert, den der Winkelhebel 10 zu überwinden hat.When energizing the proportional magnet 37 so that, so to speak, the resistance of the second spring force 15 is increased or decreased, the angle lever 10 has to overcome.

Die weitere Funktion ist ähnlich wie in Fig. 2.The other function is similar to in Fig. 2 ,

In der Ausführungsform in Fig. 4 ist weder eine elektrische Leistungsvorstellung vorgesehen, noch eine Verarbeitung eines Lastdrucksignals. Bis auf die Hauptstufe 22" entspricht der Aufbau weitgehend den von Fig. 2. Im Unterschied zu Fig. 2 ist jedoch die Hauptstufe 22" als 3/2-Wegeventil, beispielsweise in Schieberbauweise mit den beiden Druckvorsteuerungen 21, 23 ausgelegt, und ist die Leitung 25 direkt an den dritten Anschluss angeschlossen, so dass der N-Regler N nur nach Maßgabe zwischen den Kräften in den Druckvorsteuerungen 21, 23 und der ersten Federkraft 24 die Beaufschlagung der anderen Stellkolbenfläche 6 aus dem Druck in der Hauptleitung 9 regelt.In the embodiment in FIG Fig. 4 neither an electric power concept is provided, nor a processing of a load pressure signal. Except for the main stage 22 ", the structure largely corresponds to that of Fig. 2 , In contrast to Fig. 2 However, the main stage is 22 "designed as a 3/2-way valve, for example in spool design with the two pressure pilot controls 21, 23, and the line 25 is connected directly to the third terminal, so that the N-controller N only in accordance with between the forces in the pressure pilot controls 21, 23 and the first spring force 24, the admission of the other actuating piston surface 6 from the pressure in the main line 9 controls.

Auch in der Ausführungsform in Fig. 4 ist der Tastkolben 13 in das Widerlager 11 integriert, um dessen Rolle 12 zu beaufschlagen, und wird der Tastkolben aus der Kammer 4 mit dem Druck in der Hauptleitung 8 beaufschlagt.Also in the embodiment in Fig. 4 the feeler piston 13 is integrated into the abutment 11 to act on its role 12, and the probe piston from the chamber 4 is acted upon by the pressure in the main line 8.

In den Ausführungsformen der Fig. 2 bis 4 könnte alternativ die Anordnung des Widerlagers 11 und des Tastkolbens 13 wie in Fig. 1 verwendet werden.In the embodiments of the Fig. 2 to 4 Alternatively, the arrangement of the abutment 11 and the sensing piston 13 as in Fig. 1 be used.

Da das Mehrwege-Ventil 14 nur mit dem geminderten Druck zurechtzukommen braucht, kann es klein und kostengünstig ausgebildet werden und ist auch die zweite Federkraft 15 moderat. Dies gilt auch für die elektrische Leistungsvorstellung in Fig. 3, bei der das Proportional-Druckbegrenzungsventil 36 nur in einem Steuerleitungskreis enthalten ist, der geminderten Druck führt.Since the multi-way valve 14 only needs to cope with the reduced pressure, it can be made small and inexpensive, and also the second spring force 15 is moderate. This also applies to the electric power concept in Fig. 3 in which the proportional pressure relief valve 36 is included only in a control line circuit that results in reduced pressure.

Claims (12)

  1. Axial piston pump (1) having first and second differently dimensioned set piston surfaces (3, 6), a first regulator (N) having a multi-path multi-position main stage (22, 22', 22") which is pressure pilot-controlled against a first spring force (24) on a pressure pilot control (23) at least from the delivery pressure in a main line (8) connected to the delivery side (8') of the axial piston pump (1), and a second regulator (L) having a multi-way valve (14) which can be adjusted against a second spring force (15) via a pivotable angle lever (10), the angle lever (10) being acted upon by an abutment (11), which can be moved relative to the angle lever (10) by means of a set piston surface (6), and by a sensing piston (13) which is acted upon by the delivery pressure, and the delivery side (8') of the axial piston pump (1) is connected via the main line (8) at least to the pressure pilot control (23) of the main stage, an input of the main stage (22, 22', 22") and the sensing piston (13), characterized in that the main line (8) is connected to a pressure-reducing valve (17), with which a reduced control pressure can be set at an input of the multi-way valve (14) from the delivery pressure in the main line (8) with the multi-way valve (14) adjusted by the angle lever (10) against the second spring force (15), from which the adjusted multi-way valve (14) generates control pilot pressure for a regulating pressure pilot control (21) of the main stage (22, 22', 22") additionally and parallel to the pressure pilot control (23) by the delivery pressure at the pressure pilot control (23).
  2. Axial piston pump according to claim 1, characterized in that a tank line (9) is connected at least to the multi-way valve (14) and the main stage (22, 22', 22"), and in that the delivery pressure can be applied to one set piston surface (3) from the main line (8) and pressure can be applied to the other set piston surface (6) by way of the main stage (22, 22', 22") in the form of bar pressure or pressure relief.
  3. Axial piston pump according to claim 1, characterized in that the main stage (22, 22', 22") is a 3/2-way, 4/2-way or 3/3-way valve, preferably in slide valve design, with a shut-off middle position, and the multi-way valve (14) is a 3/2-way valve, wherein, preferably, the main stage (22, 22', 22") can be acted upon by the first spring force (24) to a switch position in which the other set piston surface (6) is relieved to the tank line (9) and the multi-way valve (14) can be acted upon by the second spring force (15) to a switch position in which the regulating pressure pilot control (21) is connected to the tank line (9).
  4. Axial piston pump according to claim 1, characterized in that the other set piston surface (6) is the larger and displaces the axial piston pump (1) in the direction of zero or minimum delivery.
  5. Axial piston pump according to claim 1, characterized in that the pressure pilot control (23) in the main stage has a first considerably smaller loading area than a second loading area of the regulating pressure pilot control (21) of the main stage.
  6. Axial piston pump according to claim 5, characterized in that the first loading surface of the pressure pilot control (23) is arranged on a pin connected to a valve element and the second loading surface is arranged in an annular chamber loading the valve element.
  7. Axial piston pump according to at least one of the preceding claims, characterized in that a line (25) running between the main stage (22, 22', 22") and the other set piston surface (6) is connected to the tank line (9) via a throttle (26).
  8. Axial piston pump according to at least one of the preceding claims, characterized in that for the purpose of electrical power adjustment of the axial piston pump (1) for pressure increase or for pressure reduction at the regulating pressure pilot control (21) of the main stage (22, 22', 22") from the reduced pressure of the pressure reducing valve (17) a proportional pressure relief valve (36), preferably a 3/2-way valve, is associated with the second regulator (L) downstream of the pressure reducing valve (17).
  9. Axial piston pump according to claim 8, characterized in that an input port of the proportional pressure relief valve (36) is connected to the output port of the pressure reducing valve (17), an output port of the proportional pressure relief valve (36) is connected via a throttle (41) to the spring side of the multi-way valve (14) and/or via another throttle (42) to an auxiliary piston surface (39) for loading the angle lever (10) against the second spring force (15), and a second port of the proportional pressure relief valve (36) is connected to the tank line (9).
  10. Axial piston pump according to at least one of the preceding claims, characterized in that, for an LS function in the first regulator (N), a 3/2-way valve (31) is assigned to the main stage (22, 22', 22"), the first port of which is connected to the main line (8), the second port of which is connected to the tank line (9) and the third port of which is connected to the line (25) to the other set piston surface (6), and which is acted upon by a spring (38) to a switch position, in which the first port is shut off and the second and third ports are connected, and which has a pressure pilot control (34) on the spring side in conjunction with an LS port (30) of the first regulator (N) and a pressure pilot control (33) opposite the spring side in conjunction with the main line (8).
  11. Axial piston pump according to claim 1, characterized in that the sensing piston (13) is accommodated in the abutment (11), which acts on the angle lever (10), of the one set piston surface (3) and can be acted upon, preferably via a pressure chamber (4) containing the one set piston surface (3), by the delivery pressure from the main line (8).
  12. Axial piston pump according to claim 11, characterized in that the abutment (11) is a roller plunger, and in that, preferably, the sensing piston (13) in the roller plunger acts on the roller (12) which is movable relative to the roller plunger and which runs on an arm of the angle lever (10).
EP15151407.2A 2015-01-16 2015-01-16 Axial piston pump Active EP3045723B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP15151407.2A EP3045723B1 (en) 2015-01-16 2015-01-16 Axial piston pump

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP15151407.2A EP3045723B1 (en) 2015-01-16 2015-01-16 Axial piston pump

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EP3045723A1 EP3045723A1 (en) 2016-07-20
EP3045723B1 true EP3045723B1 (en) 2019-04-10

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Publication number Priority date Publication date Assignee Title
JP6913527B2 (en) 2017-06-22 2021-08-04 株式会社小松製作所 Hydraulic pumps and motors
CN117189456B (en) * 2023-11-07 2024-04-16 华侨大学 Radial plunger hydraulic device based on sliding sleeve reversing and working method

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Publication number Priority date Publication date Assignee Title
DE3742111A1 (en) * 1987-04-02 1989-06-29 Brueninghaus Hydraulik Gmbh CONTROL DEVICE FOR AT LEAST TWO HYDROSTATIC MACHINES VARIABLE CONVEYORS OR CONNECTED TO A COMMON WORKING PRESSURE LINE. SWALLOWING VOLUME
DE19808127C2 (en) * 1998-02-26 1999-12-09 Brueninghaus Hydromatik Gmbh Power control device

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Title
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