EP3045723A1 - Pompe à pistons axiaux - Google Patents

Pompe à pistons axiaux Download PDF

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Publication number
EP3045723A1
EP3045723A1 EP15151407.2A EP15151407A EP3045723A1 EP 3045723 A1 EP3045723 A1 EP 3045723A1 EP 15151407 A EP15151407 A EP 15151407A EP 3045723 A1 EP3045723 A1 EP 3045723A1
Authority
EP
European Patent Office
Prior art keywords
pressure
piston pump
axial piston
main stage
line
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP15151407.2A
Other languages
German (de)
English (en)
Other versions
EP3045723B1 (fr
Inventor
Georg Jemüller
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.)
Hawe Hydraulik SE
Original Assignee
Hawe Hydraulik SE
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Filing date
Publication date
Application filed by Hawe Hydraulik SE filed Critical Hawe Hydraulik SE
Priority to EP15151407.2A priority Critical patent/EP3045723B1/fr
Publication of EP3045723A1 publication Critical patent/EP3045723A1/fr
Application granted granted Critical
Publication of EP3045723B1 publication Critical patent/EP3045723B1/fr
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, 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
    • F04B49/002—Hydraulic systems to change the pump delivery
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
    • F03C1/00—Reciprocating-piston liquid engines
    • F03C1/02—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders
    • F03C1/06—Reciprocating-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
    • F03C1/0678—Control
    • F03C1/0686—Control by changing the inclination of the swash plate
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/26—Control
    • F04B1/28—Control of machines or pumps with stationary cylinders
    • F04B1/29—Control of machines or pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
    • F04B1/295—Control 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/26—Control
    • F04B1/30—Control of machines or pumps with rotary cylinder blocks
    • F04B1/32—Control of machines or pumps with rotary cylinder blocks by varying the relative positions of a swash plate and a cylinder block
    • F04B1/324—Control 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, 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
    • F04B49/08—Regulating by delivery pressure

Definitions

  • the invention relates to an axial piston pump specified in the preamble of claim 1. Art.
  • bottom axial piston pump either with the controller with the plate LP or the controller with the Characteristic LLSP (with a load-sensing or load pressure signal connection) known axial piston pump is the MehrWege valve in the L-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 N-controller may be associated with a proportional pressure relief valve.
  • 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 to move, or in the case of a load to be moved, the axial piston pump so quickly restores 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 pilot control pressure adjusts the main stage with the pressure feedforward control from the main line, eg to guide hydraulic medium with low throttling to the other actuating piston surface. Thanks to the pressure reducing valve results in a precisely pre-determinable, sensitive control behavior of the controller, with only a small amount of control of the hydraulic fluid can be moved at low pressures in a main part of the hydraulic circuit.
  • the main advantages of the controller are, in addition to the exactly predictable control behavior, improved efficiency and low mechanical stress on 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 them 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 parallel to the pressure feedforward control from the main line to a pressurized with the Regelvor queen domestic control.
  • the Regelvor suittik is generated by the multi-way valve depending on the mechanical operation by the angle lever from the reduced pressure, which needs to be only about 30 bar, for example, at a maximum delivery pressure between 250 and 350 bar, for example.
  • 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, is connected to the control pressure pilot control of the main stage with the tank line ,
  • 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)
  • Fluid-Pressure Circuits (AREA)
  • Control Of Positive-Displacement Pumps (AREA)
EP15151407.2A 2015-01-16 2015-01-16 Pompe à pistons axiaux Active EP3045723B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP15151407.2A EP3045723B1 (fr) 2015-01-16 2015-01-16 Pompe à pistons axiaux

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP15151407.2A EP3045723B1 (fr) 2015-01-16 2015-01-16 Pompe à pistons axiaux

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

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11293417B2 (en) 2017-06-22 2022-04-05 Komatsu Ltd. Hydraulic pump and motor
CN117189456A (zh) * 2023-11-07 2023-12-08 华侨大学 基于滑套换向的径向柱塞液压装置及工作方法

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3742111A1 (de) * 1987-04-02 1989-06-29 Brueninghaus Hydraulik Gmbh Regeleinrichtung fuer wenigstens zwei mit einer gemeinsamen arbeitsdruckleitung in verbindung stehende hydrostatische maschinen veraenderlichen foerder- bzw. schluckvolumens
EP0939225A2 (fr) * 1998-02-26 1999-09-01 Brueninghaus Hydromatik Gmbh Dispositif de contrÔle de puissance pour plusieurs pompes hydrostatiques à débit variable

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3742111A1 (de) * 1987-04-02 1989-06-29 Brueninghaus Hydraulik Gmbh Regeleinrichtung fuer wenigstens zwei mit einer gemeinsamen arbeitsdruckleitung in verbindung stehende hydrostatische maschinen veraenderlichen foerder- bzw. schluckvolumens
EP0939225A2 (fr) * 1998-02-26 1999-09-01 Brueninghaus Hydromatik Gmbh Dispositif de contrÔle de puissance pour plusieurs pompes hydrostatiques à débit variable

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11293417B2 (en) 2017-06-22 2022-04-05 Komatsu Ltd. Hydraulic pump and motor
CN117189456A (zh) * 2023-11-07 2023-12-08 华侨大学 基于滑套换向的径向柱塞液压装置及工作方法
CN117189456B (zh) * 2023-11-07 2024-04-16 华侨大学 基于滑套换向的径向柱塞液压装置及工作方法

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