EP1118771A2 - Dispositif de régulation de puissance - Google Patents

Dispositif de régulation de puissance Download PDF

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Publication number
EP1118771A2
EP1118771A2 EP00127378A EP00127378A EP1118771A2 EP 1118771 A2 EP1118771 A2 EP 1118771A2 EP 00127378 A EP00127378 A EP 00127378A EP 00127378 A EP00127378 A EP 00127378A EP 1118771 A2 EP1118771 A2 EP 1118771A2
Authority
EP
European Patent Office
Prior art keywords
piston
control device
power control
control
operating pressure
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
EP00127378A
Other languages
German (de)
English (en)
Other versions
EP1118771A3 (fr
EP1118771B1 (fr
Inventor
Gerhard Beutler
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.)
Brueninghaus Hydromatik GmbH
Original Assignee
Brueninghaus Hydromatik GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Brueninghaus Hydromatik GmbH filed Critical Brueninghaus Hydromatik GmbH
Publication of EP1118771A2 publication Critical patent/EP1118771A2/fr
Publication of EP1118771A3 publication Critical patent/EP1118771A3/fr
Application granted granted Critical
Publication of EP1118771B1 publication Critical patent/EP1118771B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • 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
    • F04B49/002—Hydraulic systems to change the pump delivery

Definitions

  • the invention relates to a power control device for Controlling the performance of a piston machine according to the Preamble of claim 1.
  • a control device for controlling an adjustable Hydraulic pump according to the preamble of claim 1 goes from EP 0 149 787 B2.
  • the object of the present invention is therefore a Power control device specify which with low Construction work and using an existing one Pump can be realized with adjustment.
  • the task is characterized by the characteristic features of the Claim 1 in connection with the generic Features resolved.
  • the power controller according to the invention with the characteristic Features of claim 1 have over that from EP 0 149 787 B2 known control device the advantage that Regulator separately for its design before installation different services can be set. As well can adjust the power during operation an actuator that is easily accessible, be readjusted.
  • Control device as a prefabricated overall component in one For this purpose, there is a recess in the piston machine housing to use.
  • the performance curve can be achieved by simple installation variants the pump by additional external hydraulic pressure can be moved as required.
  • the invention Power control device can therefore as Total power controller can be used.
  • the low tax oil loss is also an advantage, since the power control device is directly controlled.
  • Fig. 1 shows an axial section through a Axial piston machine 1 in swash plate construction, in which a power control device 2 according to the invention is provided is.
  • the basic structure of an axial piston machine 1 in swash plate construction is known, so that the following description on the essential components can restrict.
  • a shaft 3 is on a first bearing 4 and on one second bearing 5 in a housing 6 of the axial piston machine 1 rotatably mounted.
  • the housing 6 of the axial piston machine 1 is divided into a base body 6a and one with the Base body 6a screwed cover body 6b.
  • a cylinder drum 7 is rotationally fixed to the shaft 3 connected.
  • the cylinder drum 7 are on a Pitch circle offset cylinder bores 8, in which pistons 9 are axially displaceable.
  • the pistons 9 are via ball joint connections 10 with sliding shoes 11 connected and based on the sliding shoes 11 on a formed as swivel cradle swash plate 12.
  • the Swash plate 12 serves as an actuator for adjusting the Delivery volume of the axial piston machine 1.
  • the connection of the Cylinder bores 8 with a not shown High pressure line and also not shown Low pressure line takes place via a control body 13 which a kidney-shaped high pressure opening 14 and also one kidney-shaped low pressure opening 15.
  • the hub of the Piston 9 in the cylinder bores 8 is through the Swivel angle ⁇ of the swash plate 12 predetermined.
  • Swashplate 12 designed as a swivel cradle is shown in FIG. 1 both in their neutral position and in one around the Swivel angle ⁇ pivoted position shown twice.
  • the cylinder drum 7 is by means of a spring 22 on the Control body 13 held in contact. To do this, the Spring 22 via a first ring 23 on the cylinder drum 7 and via a second ring 24 on the shaft 3.
  • the Cylinder drum 7 is opposite to the fixed shaft 3 a key-groove connection axially movable.
  • Die Power control device 2 is in a receiving bore 16 of the housing 6 integrated and consists of a Ball joint slide connection 17 with the swash plate 12 connected actuating piston 18, which in the receiving bore 16 is axially guided, one in the receiving bore 16th used control valve 19.
  • the control valve 19 and Actuating pistons 18 are axially offset in the receiving bore 16 arranged to each other.
  • a control valve for a Flow control can be used in the same way, so as is known from DE 199 49 169 A1.
  • the Control valves are therefore modular, depending on the application interchangeable.
  • a spherical sliding block 22 sliding on, which together with one in FIG. 1 shown spherical recess 23 of the swash plate 12 the ball joint sliding connection 17 forms.
  • the sliding block 22 could also be reversed slide against the swash plate 12 and the spherical Recess 23 may be formed in the actuating piston 18.
  • FIG. 2 The first embodiment of the invention Power control device 2 is enlarged in FIG. 2 shown.
  • Fig. 1 are the same Identify elements with matching reference numerals in order to facilitate the assignment.
  • the adjusting piston 18 is cup-shaped and has a central fastening wick 30, which a Has thread.
  • a threaded section 31 an extension 32 screwed, which is in axial direction through the control piston 18, the control piston 20, a second spring mount 33 and return springs 50, 53 extends.
  • a valve sleeve 35 connects to the actuating piston 18, which a first operating pressure port 36, which with the Operating pressure of the piston engine 1 is connected, and a Has tank connection 37.
  • the control piston 20 is in radial direction surrounded by the valve sleeve 35 and will penetrated by the extension 32 by a Recess 41 of the control piston 20 is passed through.
  • the control piston 20 has a first groove 38, which with the first operating pressure port 36 is connected and on which is a first contact surface 39 for the operating pressure the piston engine 1 is formed. About the first The operating pressure of the piston engine 1 is exerted on the contact surface 39 an axial force on the control piston 20.
  • a second Groove 40 in the control piston 20 is connected to the tank connection 37 connected.
  • the actuating piston 18 has an actuating pressure chamber 42, which is designed as a recess in the actuating piston 18.
  • the Signal pressure chamber 42 stands over axial bores 59a and at least one radial bore 59b in the valve sleeve 35 a first control edge 43 and a second control edge 44 of the control piston 20 in connection.
  • a first control edge 43 and a second control edge 44 of the control piston 20 in connection.
  • radial bore 59b over the first Control edge 43 with the first groove 38 or via the second Control edge 44 connected to the second groove 40.
  • Position of the control piston 20 is therefore the pressure in the Signal pressure chamber either increased or decreased.
  • the Signal pressure chamber 42 is in the valve sleeve 35 Integrated discharge throttle 45 with the tank connection 37 connected so that the actuating piston 18 when pivoting to the maximum displacement volume, the hydraulic fluid from the Signal pressure chamber displaced.
  • the control piston 20 strikes with a first end 46 a central recess 47 of the valve sleeve 35 and is at a second end 48 with the second spring holder 33 connected, which has an outside step 49.
  • a first return spring 50 is supported, which in is penetrated in the axial direction by the extension 32.
  • the first return spring 50 is supported on one end outer support sleeve 52a, which with an inner Support sleeve 52b forms a first spring holder 51.
  • At the inner support sleeve 52b supports a second Return spring 53 from.
  • the first spring holder 51 is in contact a lock nut 54 on which on a thread 55 on End of the extension bolt 32 is screwed on.
  • the lock nut 54 is an adjustment of the Spring tension of the return springs 50 and 53 through Screw the spring holder 51 in relation to the extension 32 allows.
  • the return springs 50 and 53 and the first Spring receptacles 51 are in a spring receiving space 34 arranged and are surrounded by a spring sleeve 56.
  • This is designed to be removable and with a sealing element 57, e.g. B. an O-ring sealed.
  • Another sealing element 58 which can also be designed as an O-ring, seals the power control device 2 against the Piston engine 1 from.
  • the mode of operation of the power control device 2 is based on the background that the output of the Piston machine 1 from the swivel angle ⁇ of the swash plate 12 and is dependent on the working pressure. Is the swash plate 12 relative to axis 3 at a right angle ( ⁇ 0 °), the piston machine 1 is idling. Once the The angle ⁇ becomes larger, the piston machine 1 begins To promote hydraulic fluid. To regulate the delivery rate or limit, the control valve 19, the control piston 18 so that the swash plate 12 under a Angle ⁇ , from 0 ° to a certain maximum angle is enough, is tilted. The maximum angle is determined by the Basic position of the actuating piston 18 defined. The Piston machine 1 always starts at this maximum angle, to build up enough pressure.
  • control piston 20 leads to a larger opposite movement of the actuating piston 18, which presses against the swash plate 12 and thereby the swivel angle ⁇ is reduced.
  • the pressure in the signal pressure chamber 42 is thereby Control valve 19 on a between tank pressure and Operating pressure lying signal pressure regulated. As long as the Signal pressure chamber 42 in connection with the first groove 38 stands, hydraulic fluid is under operating pressure in the Signal pressure chamber 42 pressed, whereby the actuating piston 18 the Swash plate 12 in the direction of a smaller swivel angle ⁇ emotional.
  • the power control device 2 leads to a approximately constant maximum power of the piston engine 1.
  • the assumed values of pressure and delivery volume are in a pressure-delivery volume diagram (p-V diagram) a straight line, the slope of which in this area is approximately the Rise of the theoretical power hyperbole in the p-V diagram corresponds.
  • FIG 3 is a second embodiment of the power control device 2 according to the invention shown, which differs from the first embodiment by a differs second operating pressure port 60, which with the operating pressure of another, not shown Piston machine is connected.
  • the otherwise identical execution of the Power control device 2 is therefore not in the following described again.
  • the exemplary embodiment is in FIG. 3 provided with identical reference symbols in order to assign them to facilitate.
  • Control piston 20 has a third groove 61, which with the second operating pressure port 60 is connected and on which has a second contact surface 62 for the operating pressure the other piston machine is formed. About the second Operating surface 62 exerts the operating pressure of the others Piston machine another axial force on the Control piston 20 out.
  • a corresponding choice of the individual Operating pressures or the individual delivery volumes of the Piston machine 1 and the other, not shown Piston machine leads to the fact that the invention Power control device 2 also as a total power controller can be carried out, the sum of the services of Piston machine 1 and the other, not shown Piston engine is limited to a predetermined maximum.
  • the invention is not shown on the Embodiments limited, but can also with a Power control device 2 in a different design or Axial piston machines 1 in a different design are used come. It should be emphasized that the travel of the control piston 18th is independent of the travel of the control piston 20 and despite a very slight adjustment of the Control piston 20 a much larger travel range Control piston 18 can be reached.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Actuator (AREA)
EP20000127378 2000-01-18 2000-12-13 Dispositif de régulation de puissance Expired - Lifetime EP1118771B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE2000101826 DE10001826C1 (de) 2000-01-18 2000-01-18 Vorrichtung zum Regeln der Leistung einer verstellbaren Kolbenmaschine
DE10001826 2000-01-18

Publications (3)

Publication Number Publication Date
EP1118771A2 true EP1118771A2 (fr) 2001-07-25
EP1118771A3 EP1118771A3 (fr) 2005-10-19
EP1118771B1 EP1118771B1 (fr) 2006-08-16

Family

ID=7627827

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20000127378 Expired - Lifetime EP1118771B1 (fr) 2000-01-18 2000-12-13 Dispositif de régulation de puissance

Country Status (2)

Country Link
EP (1) EP1118771B1 (fr)
DE (2) DE10001826C1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2008138603A1 (fr) 2007-05-14 2008-11-20 Robert Bosch Gmbh Machine à pistons axiaux pourvue d'un dispositif de rappel
WO2014166691A1 (fr) * 2013-04-08 2014-10-16 Robert Bosch Gmbh Machine à piston axiaux
US20150337829A1 (en) * 2014-05-22 2015-11-26 Robert Bosch Gmbh Adjustment Device for a Hydrostatic Piston Machine, and Hydrostatic Axial Piston Machine

Families Citing this family (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10341331B3 (de) * 2003-09-08 2005-05-25 Brueninghaus Hydromatik Gmbh Leistungsregelvorrichtung
DE102009006909B4 (de) 2009-01-30 2019-09-12 Robert Bosch Gmbh Axialkolbenmaschine mit reduzierter Stelldruckpulsation
DE102013214861A1 (de) 2012-08-16 2014-05-22 Robert Bosch Gmbh Verstellvorrichtung für eine hydrostatische Pumpe und hydrostatische Pumpe
DE102012022997A1 (de) 2012-11-24 2014-05-28 Robert Bosch Gmbh Verstelleinrichtung für eine Hydromaschine und hydraulische Axialkolbenmaschine
DE102014202411A1 (de) 2014-02-11 2015-08-13 Robert Bosch Gmbh Elektrisch angesteuertes Druckregelventil für eine verstellbare hydrostatische Pumpe und eine verstellbare hydrostatische Pumpe mit einem Druckregelventil
DE102014202412A1 (de) 2014-02-11 2015-08-13 Robert Bosch Gmbh Elektrisch angesteuertes Druckregelventil für eine verstellbare hydrostatische Pumpe und verstellbare hydrostatische Pumpe mit einem Druckregelventil
DE102014202413A1 (de) 2014-02-11 2015-08-13 Robert Bosch Gmbh Elektrisch angesteuertes Regelventil für eine verstellbare hydrostatische Pumpe und verstellbare hydrostatische Pumpe
DE102014226378A1 (de) 2014-02-18 2015-08-20 Robert Bosch Gmbh Elektrisch angesteuertes Druckregelventil für eine verstellbare hydrostatische Pumpe
DE102014206755B4 (de) 2014-02-18 2024-09-19 Robert Bosch Gmbh Verstelleinrichtung einer Axialkolbenmaschine mit einem Druckmittel beaufschlagten Steuerventil
DE102015207260A1 (de) 2014-05-22 2015-11-26 Robert Bosch Gmbh Verstelleinrichtung für eine hydrostatische Kolbenmaschine und hydrostatische Axialkolbenmaschine
DE102014211202A1 (de) * 2014-06-12 2015-12-17 Robert Bosch Gmbh Hydrostatische Axialkolbenmaschine in Schrägscheibenbauweise und Lüfter mit einer hydro-statischen Axialkolbenmaschine
CH714321A1 (de) 2017-11-11 2019-05-15 Liebherr Machines Bulle Sa Verstellvorrichtung für eine Axialkolbenmaschine.
CN111710562B (zh) * 2020-06-27 2025-04-08 天水二一三电器集团有限公司 接触器的动断触头系统

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0149787A2 (fr) 1983-12-14 1985-07-31 BRUENINGHAUS HYDRAULIK GmbH Dispositif de régulation de débit pour une pompe hydraulique réglable
DE19949169A1 (de) 1999-10-12 2001-04-26 Brueninghaus Hydromatik Gmbh Verstellvorrichtung

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0059708B1 (fr) * 1980-09-12 1987-07-29 Caterpillar Inc. Commande d'utilisation de puissance pour pompes a deplacement variable
DE3200885A1 (de) * 1982-01-14 1983-07-21 Robert Bosch Gmbh, 7000 Stuttgart Leistungsregler fuer eine hydrostatische pumpe
DE3232903A1 (de) * 1982-09-04 1984-03-08 Alfred Teves Gmbh, 6000 Frankfurt Hydrostatischer antrieb
DE3935800C2 (de) * 1989-10-27 1997-03-27 Linde Ag Einstellbare Axialkolbenmaschine in Schrägscheibenbauweise
DE4141722A1 (de) * 1991-12-18 1993-06-24 Bayer Ag Isocyanat-trimerisierungskatalysator

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0149787A2 (fr) 1983-12-14 1985-07-31 BRUENINGHAUS HYDRAULIK GmbH Dispositif de régulation de débit pour une pompe hydraulique réglable
DE19949169A1 (de) 1999-10-12 2001-04-26 Brueninghaus Hydromatik Gmbh Verstellvorrichtung

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2008138603A1 (fr) 2007-05-14 2008-11-20 Robert Bosch Gmbh Machine à pistons axiaux pourvue d'un dispositif de rappel
US8418599B2 (en) 2007-05-14 2013-04-16 Robert Bosch Gmbh Axial piston machine having a return device
WO2014166691A1 (fr) * 2013-04-08 2014-10-16 Robert Bosch Gmbh Machine à piston axiaux
US20150337829A1 (en) * 2014-05-22 2015-11-26 Robert Bosch Gmbh Adjustment Device for a Hydrostatic Piston Machine, and Hydrostatic Axial Piston Machine
CN105179193A (zh) * 2014-05-22 2015-12-23 罗伯特·博世有限公司 用于静液压活塞机的调节装置和静液压轴向活塞机
US10054113B2 (en) * 2014-05-22 2018-08-21 Robert Bosch Gmbh Adjustment device for a hydrostatic piston machine, and hydrostatic axial piston machine
CN105179193B (zh) * 2014-05-22 2019-01-01 罗伯特·博世有限公司 用于静液压活塞机的调节装置和静液压轴向活塞机

Also Published As

Publication number Publication date
EP1118771A3 (fr) 2005-10-19
EP1118771B1 (fr) 2006-08-16
DE50013332D1 (de) 2006-09-28
DE10001826C1 (de) 2001-09-20

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