WO2009037069A1 - Plaque de connexion pour un moteur à pistons hydrostatique - Google Patents

Plaque de connexion pour un moteur à pistons hydrostatique Download PDF

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Publication number
WO2009037069A1
WO2009037069A1 PCT/EP2008/061120 EP2008061120W WO2009037069A1 WO 2009037069 A1 WO2009037069 A1 WO 2009037069A1 EP 2008061120 W EP2008061120 W EP 2008061120W WO 2009037069 A1 WO2009037069 A1 WO 2009037069A1
Authority
WO
WIPO (PCT)
Prior art keywords
pressure
connection plate
valve
connection
plate according
Prior art date
Application number
PCT/EP2008/061120
Other languages
German (de)
English (en)
Inventor
Michael Duerr
Original Assignee
Robert Bosch 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 Robert Bosch Gmbh filed Critical Robert Bosch Gmbh
Publication of WO2009037069A1 publication Critical patent/WO2009037069A1/fr

Links

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
    • 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
    • F04B1/14—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 having stationary cylinders
    • F04B1/141—Details or component parts
    • F04B1/145—Housings
    • 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 a connection plate for a hydrostatic piston machine with a connection plate housing, in which at least one high-pressure connection for connecting the hydrostatic piston machine with a hydraulic circuit is formed.
  • a hydrostatic axial piston machine in which a control valve interacts with an adjusting device.
  • the adjusting piston of the adjusting device engages on a pivotable
  • a hydraulic force is adjustable to the actuator piston.
  • a control pressure chamber is variably connected by the control valve with a delivery-side working line of the hydrostatic piston engine or with a tank volume. In the connection between the control valve and the tank volume, a pressure control valve is arranged.
  • the pressure control valve is acted upon against the force of a spring with the delivery-side pressure of the pump. If this pressure exceeds the pressure set by the spring, the tank connection of the control valve is connected to the delivery-side working line of the hydraulic pump. As a result, the swash plate of the hydraulic pump is adjusted in the direction of vanishing delivery volume.
  • the known axial piston machine has the disadvantage that the pressure regulating valve is provided as an external valve. To allow a connection between the tank connection of the control valve and the delivery-side working line, therefore, a considerable construction effort with multiple components is possible. In addition, long cable paths caused by the external arrangement of the pressure control valve. This degrades the response.
  • connection plate with an integrated arrangement of the pressure control valve.
  • the object is achieved by the connection plate according to the invention with the features of claim 1.
  • connection plate according to the invention for a hydrostatic piston machine has a connection plate housing, in which at least one high-pressure connection for connecting the hydrostatic piston machine to a hydraulic circuit is formed.
  • this connection plate housing a pressure regulator is arranged.
  • the connection plate housing further comprises a connection channel for an adjusting device is formed, which is connected by means of the pressure regulator variable with the high pressure port or a tank volume.
  • connection plate housing has the advantage that only short cable paths in the connection plate are required.
  • a connection channel is formed in the connection plate housing, via which the adjusting device can be connected either to a tank volume or to a high-pressure connection of the pump.
  • the short lines reduce the machining effort considerably and at the same time improve the slew time.
  • the adjusting device preferably comprises a control valve.
  • the connection channel then leads to the control valve of the adjusting device.
  • the adjusting device of the axial piston machine has a control valve, which is preferably arranged in the connection plate housing.
  • Control valve is a control pressure chamber of the adjusting device variably connected to a high pressure port or the connection channel of the terminal plate housing.
  • the arrangement of the control valve of the adjusting device in the connection plate housing a compact structural unit of the connection plate and thus ultimately the hydraulic pump allows.
  • the individual channels, which are provided for driving the control valve, are extremely short. The dynamics of the hydrostatic piston engine is thus improved.
  • connection plate housing preferably has a high pressure port and a low pressure port, wherein the pressure regulator between the control valve of the actuator and the high pressure and
  • Low pressure connection is arranged.
  • the valve axis of the pressure regulator is formed approximately perpendicular to the center axes of the high pressure port and the low pressure port and the axis of the control valve.
  • This arrangement has the advantage that the available space of the connection plate can be advantageously used between the high-pressure connections, which are often formed approximately centrally on the connection plate, and the laterally arranged control valve.
  • the respective connection of the control valve either with the high pressure side of the hydraulic pump or with the low pressure side of the hydraulic pump or the tank volume in each case via the Pressure regulator takes place.
  • the individual cable lengths are shortened.
  • the pressure regulator has a high pressure area and a low pressure area and is so in the
  • connection plate housing Used connecting plate housing, that the high-pressure region is disposed closer to the high pressure port than a low pressure port and that the low pressure region of the pressure regulator is disposed closer to the low pressure port than to the high pressure port.
  • the pressure regulator is preferably designed as a pressure control cartridge and has a valve sleeve in which a valve piston and a valve spring acting thereon are arranged.
  • the valve spring is supported at a first end on the valve piston and at its second end to a, with respect to its position relative to the valve sleeve adjustable spring bearing.
  • the pressure control cartridge can be adjusted to its set value and so the opening behavior when exceeding a certain pressure before mounting in the terminal plate housing.
  • the preassembled module is then inserted as a whole in the connection plate housing. A pressure setting of the opening pressure must be installed Pressure control cartridge not done again.
  • the valve piston can also be arranged directly in a recess of the connection plate.
  • the adjustable spring bearing is designed as pressed into the bush disc. By determining the offset in a corresponding recess of the bushing of the pressure control cartridge, the bias of the valve spring is adjusted.
  • the pressure control cartridge is preferably used in this embodiment with the adjustable spring bearing in a recess of the connection plate.
  • the pressure control cartridge is at the of the adjustable
  • connection plate housing Due to the possibility to perform a presetting of the pressure control cartridge, after the installation of the pressure control cartridge into the connection plate housing, the adjustable spring bearing no longer has to be accessible. It can thus be formed at the end facing away from a simple fixation possibility for fastening the pressure control cartridge by means of the valve sleeve in the terminal plate housing.
  • the adjustable spring bearing is designed as a plastically deformable cap. This plastically deformable cap closes the valve sleeve or the recess of the connection plate housing when the valve piston of the
  • Pressure regulator is arranged directly in the terminal plate housing.
  • the distance between the two spring bearings, ie a closed end of the deformable cap and one end of the valve piston, is adjusted by plastically deforming the cap.
  • the pressure control cartridge with the end facing away from the deformable cap in the terminal plate is used.
  • the pressure control cartridge is then fixed by means of the cap in the connection plate against unintentional release.
  • the plastically deformable cap can first be mechanically fixed to the valve bushing. For example, it is conceivable that the cap is pressed onto a correspondingly elaborate seat of the valve sleeve. In this case, a particularly simple check of the opening behavior of the preassembled pressure control cartridge is possible.
  • the adjustment of the pressure control cartridge can then be made in a dismounted state.
  • connection plate housing is preferably on the
  • Connection plate housing formed a plastically deformable portion, which surrounds a radially tapered region of the pressure control cartridge for fixing the pressure control cartridge after a forming process.
  • This tapered portion of the pressure control cartridge is formed on the valve sleeve or a tapered portion of the deformable cap.
  • Such a plastically deformable region together with a radially tapered region, either on the valve bush or in the region of the deformable cap allows a particularly simple mechanical fixation of the pressure control cartridge.
  • the plastically deformable region is applied, for example, by caulking around the radially tapered region of the pressure control cartridge.
  • the plastically deformable region surrounds a closure element, which surrounds the plastically deformable cap or z. B. may be a ball.
  • a radially sealing sealing element is between the region with which the pressure control cartridge in the
  • Terminal plate housing is fixed, and arranged in the terminal plate housing into the projecting end.
  • a radially sealing sealing element which may for example be an O-ring
  • the fixation of the pressure regulating cartridge by means of a thread in the terminal plate housing is possible.
  • the thread is not subjected to the high pressure in this case.
  • different expansions occurring with different materials of the pressure control cartridge and the connection plate housing due to temperature fluctuations do not lead to a leakage of the connection plate.
  • the connection plate housing is preferably made of an aluminum alloy and the valve bushing of the pressure control cartridge made of a steel.
  • connection plate according to the invention Preferred embodiments of the connection plate according to the invention are shown in the drawing and are explained in more detail in the following description. Show it:
  • Fig. 2 shows a first embodiment in which the
  • Pressure control cartridge is fixed by means of a screw in the terminal plate housing
  • Fig. 3 shows a second embodiment of a connection plate according to the invention, in which the
  • FIG. 4 shows a third embodiment, wherein the plastic deformation of the connection plate housing is formed in the region of a deformable cap of the pressure control cartridge.
  • FIG. 1 shows a hydrostatic pump unit 1 with a hydraulic pump 2.
  • the hydraulic pump 2 is connected to a drive shaft 3. About the drive shaft 3, which is connected to a drive motor, not shown, the hydraulic pump 2 is driven.
  • a first working channel 4 and a second working channel 5 are formed, which connect the engine with a high pressure port 6 and a low pressure port 7.
  • the high pressure port 6 and the low pressure port 7 are formed in a port plate of the hydraulic pump unit 1.
  • a working line 8, 9 is connected in each case, via which the hydraulic pump unit 1 is connected to a hydraulic circuit.
  • the hydrostatic pump unit 1 is designed to be adjustable in terms of their delivery volume, wherein the hydraulic pump 2 is provided for conveying in only one direction.
  • an adjusting device 10 is provided for adjusting the stroke volume of the hydraulic pump 2.
  • the adjusting device 10 comprises a cylinder 11, in which an adjusting piston 12 is displaceably formed.
  • the actuator piston 12 is moved by a spring in the direction of his
  • a control pressure acts on a piston surface of the actuating piston 12.
  • the actuating piston 12 moves against the force of the spring.
  • the actuating piston 12 acts with a
  • a control valve 13 is provided.
  • the control valve 13 is designed as a 3/3-way valve.
  • the control valve 13 has a valve piston which at its first end with the force of a feedback spring 15 for feedback of the position of the
  • Adjusting piston 12 is acted upon.
  • the feedback spring 15 is arranged in a control pressure chamber 16 and is supported with its first end on the piston surface of the actuating piston 12 and with its second end on the valve piston of the control valve 13 from.
  • the valve piston of the control valve 13 with the force of a proportional solenoid 14 can be acted upon.
  • the proportional solenoid 14 generates a control force on the valve piston in response to a control signal applied to the proportional solenoid 14.
  • the control pressure chamber 16 is connected to a control pressure connection of the control valve 13 via a control pressure line 17.
  • the control valve 13 is pressure balanced. For this purpose branches from the control pressure line 17 a
  • the working line connection is connected via a connecting line 18 to the working channel 4 and thus the high pressure port 6.
  • an adjustable spring 22 is provided for determining the rest position.
  • a valve piston of the pressure control valve 21 is held in a position which connects the connection channel 19 throughflow with the discharge channel 23.
  • a further connecting line 24 is provided, which likewise connects the connecting channel 19 with the tank volume 20 via two throttling points arranged in succession.
  • the discharge channel 23 opens between these two throttle points in the further connection line 24.
  • the control valve 13 In the rest position of the hydraulic pump unit 1 shown in FIG. 1, the control valve 13 is in its first end position.
  • proportional solenoid 14 When de-energized proportional solenoid 14, a force is exerted on the valve piston of the control valve 13 by the feedback spring 15, which holds the valve piston in this first end position.
  • the control pressure line 17 In this first end position, the control pressure line 17 is connected to the connection channel 19 by flow.
  • the proportional solenoid 14 If the proportional solenoid 14 is energized, the valve piston is deflected out of this rest position of the control valve 13, counter to the force of the feedback spring 15.
  • the connecting channel 18 is increasingly connected to the actuating pressure channel 17.
  • the actuating piston 12 is thereby moved in Fig.
  • Working channel 4 over a specified limit speaks to the pressure control valve 21.
  • Pressure control valve 21 has an input port and a measuring surface, which via a connecting channel branch 18 'also with the first
  • connection plate 2 shows a partial section through a connection plate according to the invention.
  • the connection plate according to the invention has a connection plate housing 25 into which a pressure control cartridge 27 for forming the Pressure control valve 21 of FIG. 1 is used and which closes a housing of the pump unit 1.
  • the connection plate housing 25 is for this purpose provided with a recess 26 in which the pressure control cartridge 27 is arranged. If, according to an alternative embodiment, the valve piston is arranged directly in a recess 26 corresponding to the recess of the connection plate housing, it is preferably hard-coated. This results in particular in a production of the connection plate made of aluminum advantages in wear resistance.
  • the pressure control cartridge 27 includes a valve sleeve 28 in which a valve piston 29 is arranged displaceably in the axial direction.
  • the valve piston 29 is in one
  • Stepped bore 30 out On the valve piston 29 areas are designed with radially different dimensions. As a result, surfaces or control edges which can be acted upon by pressures are produced on the valve piston 29, as will be explained below.
  • a Hochscherringnut 31 is formed at the outer periphery of the valve sleeve 27.
  • the high-pressure ring groove 31 communicates with a high pressure port 32 of the terminal plate housing 25 via a bore which forms the connecting channel branch 18 '.
  • the Hochyakringnut 31 is connected via two, the valve sleeve 28 penetrating transverse bores with the stepped bore 30.
  • the transverse bores are arranged axially offset in the valve bush 28 such that a connection between the high-pressure ring groove 31 and the stepped bore 30 is formed on both sides of a sealing region of the valve piston 29 cooperating with the stepped bore 30.
  • a measuring surface 33 formed on the valve piston 29 and an inlet connection with the high pressure of the hydraulic pump 2 are acted upon.
  • the pressure acting on the measuring surface 33 generates a force in the axial direction and attempts to move the valve piston 29 in FIG. 2 to the right against the force of the spring 22.
  • a first control edge 34 is formed on the valve piston 29, a first control edge 34 is formed.
  • the first control edge 34 acts in a left end position (rest position) of the valve piston 29 sealingly with the stepped bore 30 together.
  • valve piston 29 If the valve piston 29 is displaced to the right in FIG. 2 due to the hydraulic force on the measuring surface 33, the first control edge 34 releases a through-flow connection between the high-pressure ring groove 31 and a further annular groove 36 likewise formed on the outer circumference of the valve sleeve 28.
  • This further annular groove 36 is connected to the stepped bore 30 via a further transverse bore and with a connection channel 37.
  • the connection channel 37 is also designed as a bore in the connection plate housing and corresponds to the
  • a second control edge 35 is formed on the valve piston 29.
  • the first and the second control edge 34, 35 are achieved by reducing the diameter of the valve piston 29.
  • the second control edge 35 is a flow-through connection between the connection channel 37 and a
  • the Niederbuchringnut 39 free when the valve piston 29 is moved in Fig. 2 to the left. In the left end position of the valve piston 29 of the pressure control cartridge 27 so that the connection channel 37 can be flowed through connected to a housing tank volume.
  • the Niederbuchringnut 39 is for this purpose also connected to the stepped bore 30 via a transverse bore.
  • the valve piston 29 is acted upon by the force of the spring 22.
  • the spring 22 is supported on the one hand at the end of the valve piston 29 and on the other hand on an adjustable spring bearing.
  • the adjustable spring bearing is designed as a disc 40, which is pressed into an open end of the stepped bore 30.
  • volume flow compensation between the spring chamber and the Niederbuchringnut 39 can be achieved.
  • the space in front of the side facing away from the spring chamber end face of the valve piston 29 is connected via an axial bore in the valve piston with the spring chamber, so that there is also low pressure. Except for the annular measuring surface 33 of the valve piston 29 is thus pressure balanced.
  • a threaded connection 41 between the valve sleeve 28 and the terminal plate housing 25 is formed.
  • the preassembled pressure control cartridge 27 is inserted into the recess 26 and screwed there for fixing via the threaded connection 41.
  • the valve sleeve 28 is preferably made of a steel, while the terminal plate housing 25 is made of an aluminum material. In order to prevent a pressure load of the threaded connection 41, the valve sleeve 28 is in a region which is between the threaded connection 41 and in the
  • At least one radial sealing element is provided at the terminal plate housing 25 in the projecting end, on which the spring space is formed.
  • This radial sealing element is for example an O-ring, which is inserted into a first sealing groove 42.
  • a second sealing groove 43 and a third sealing groove 44 is provided.
  • the high pressure area of the pressure control cartridge 27 is thus sealed on the one hand via an O-ring in the first seal groove 42 and a second O-ring in the second seal groove 43.
  • the area around the connecting channel 37 is sealed by the O-ring in the second sealing groove 43, and a third O-ring in the third sealing groove 44, so that even with a deflection of the valve piston 29 in FIG. 2 to the right, then high pressure port 37 is sealed from the low pressure region of the pressure control cartridge 27.
  • the high-pressure region of the pressure-regulating cartridge 27 is thus arranged closer to the high-pressure port 32 than to a low-pressure port 45, which is likewise formed in the port plate housing 25.
  • the low pressure region of the pressure regulating cartridge 27 is closer to the low pressure port 45 than to the
  • High pressure port 32 is arranged. Such an arrangement is achieved by the high pressure port 32 and the low pressure port 45 are introduced with parallel symmetry axes in the terminal plate housing 25.
  • the pressure control cartridge 27 is formed between the high-pressure port 32 and the low-pressure port 45 as well as the control valve 13 to be inserted into the port plate housing 25 on the other side of the pressure control cartridge 27.
  • This arrangement has the advantage that the connections of the pressure control cartridge 27 are formed with the high pressure port 32 and the low pressure port 45 and the control valve 13 through the connection channel 37 on opposite sides of the pressure control cartridge 27.
  • FIG. 3 shows a further possible fixation of the pressure regulating cartridge 27 'in the connection plate housing 25'. Identical elements are provided with identical reference numerals. In order to avoid unnecessary repetition, reference is made in this regard to the above statements with reference to FIG. 2.
  • a radially tapered region is provided on the valve sleeve 28 'instead of the threaded connection 41.
  • the radially tapered region is formed in the illustrated embodiment of FIG. 3 in the form of a hemispherical end 46 of the valve sleeve 28 '.
  • the length of the valve sleeve 28 ' is dimensioned so that the hemispherical end 46 of the valve sleeve 28' after insertion into the recess 26 within the terminal plate housing 25 'is located. To the Recess 26 around is at the end to which the recess 26 is open, in the
  • Connection plate housing 25 ' has a groove 47 introduced. Through this groove 47, a cylindrical portion around the recess 26 is formed, which is plastically deformed and applied to the radially tapered end of the valve sleeve 28 'and this region of the valve sleeve 28' thus includes.
  • plastically deformed and the pressure control cartridge 27 'so caulked in the terminal plate housing 25' are further advantages that not only a mechanical fixation but at the same time a seal of the pressure control cartridge 27 'against the
  • Terminal plate housing 25 ' is achieved.
  • the first sealing groove 42 can thus be omitted.
  • the pressure regulating cartridge 27 or 27 ' is inserted into the connection plate housing 25 or 25' from the side of the high-pressure connection 32.
  • the pressure control cartridge 27 and 27 'with the spring 22 is inserted into the terminal plate housing 25 and 25' ahead.
  • the pressure control cartridge 27 could also be inserted from the opposite side into the terminal plate housing 25 '.
  • the radially tapered region could then be formed in the region of the spring chamber.
  • the pressed-in disc 40 would then remain accessible even in the assembled state of the pressure control cartridge 27 'and could be readjusted.
  • FIG. 4 shows a further example with a caulked pressure control cartridge 27, in which also a subsequent adjustment of the
  • the plastically deformable cap 48 has a radially tapered region 49, which is surrounded by a plastically deformed region of the connection plate housing 25 '' and thus mechanically fixes the pressure control cartridge 27 '' in the connection plate housing 25 '' and simultaneously seals.
  • the plastically deformable cap 48 if a pre-assembly of the pressure control cartridge 27 '' is desired, for example, by a press connection at the open end with the valve sleeve 28 '' be pressed. To adjust the spring bias of the spring 22, the closed end of the cap 48 is plastically deformed. Inside the cap 48 is also a
  • Washer 40 ' is provided, on which the spring 22 abuts.
  • the position of the disc 40 ' is determined by deforming the closed end of the cap 48.
  • the configuration of the connection plate housing 25 '' in the area around the receiving recess 26 ' corresponds to that explained with reference to FIG. 3.
  • the invention is not limited to the illustrated embodiments. Rather, combinations of individual features of the embodiments are possible. This also applies, above all, to the transmission of features shown in the examples to the pressure control cartridges to a design with a valve piston arranged directly in the connection plate.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)

Abstract

L'invention concerne une plaque de connexion pour un moteur à pistons hydrostatique (1), comportant un boîtier de plaque de connexion (25) dans lequel au moins une connexion haute pression (32) est conçue pour la connexion du moteur à pistons hydrostatique (1) à un circuit hydraulique. Le boîtier de plaque de connexion (25) contient une cartouche de régulation de pression (27) permettant de connecter une soupape de régulation d'un dispositif de réglage de façon variable à la connexion haute pression (32) ou à un volume de réservoir.
PCT/EP2008/061120 2007-09-18 2008-08-26 Plaque de connexion pour un moteur à pistons hydrostatique WO2009037069A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE200710044451 DE102007044451A1 (de) 2007-09-18 2007-09-18 Anschlussplatte für eine hydrostatische Kolbenmaschine
DE102007044451.8 2007-09-18

Publications (1)

Publication Number Publication Date
WO2009037069A1 true WO2009037069A1 (fr) 2009-03-26

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ID=40112316

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2008/061120 WO2009037069A1 (fr) 2007-09-18 2008-08-26 Plaque de connexion pour un moteur à pistons hydrostatique

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DE (1) DE102007044451A1 (fr)
WO (1) WO2009037069A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2011127883A1 (fr) * 2010-04-16 2011-10-20 Robert Bosch Gmbh Plaque de raccordement pour une machine hydrostatique à piston

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102009037733B4 (de) 2009-08-17 2021-12-09 Robert Bosch Gmbh Regelventilanordnung und Verstellpumpe
DE102010048068B4 (de) 2010-04-16 2022-11-10 Robert Bosch Gmbh Ventilanordnung
DE102010035457A1 (de) * 2010-08-26 2012-03-01 Robert Bosch Gmbh Ventilanordnung, Anschlussplatte für eine hydrostatische Kolbenmaschine und hydrostatische Kolbenmaschine
DE102013224112B4 (de) 2013-11-26 2024-01-18 Robert Bosch Gmbh Hydromaschine in Axialkolbenbauweise mit einer durch einen Proportionalmagneten verstellbaren Schrägscheiben-Stelleinrichtung
DE102017213458A1 (de) * 2017-08-03 2019-02-07 Robert Bosch Gmbh Hydrostatische Axialkolbenmaschine mit Leistungsbegrenzung

Citations (7)

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Publication number Priority date Publication date Assignee Title
US3169674A (en) * 1962-04-05 1965-02-16 Lund Jens Pump with delivery adjustment
US4157233A (en) * 1975-07-04 1979-06-05 Daikin Kogyo Co., Ltd. Variable delivery hydraulic pump
US4379389A (en) * 1980-09-12 1983-04-12 Caterpillar Tractor Co. Horsepower consumption control for variable displacement pumps
DE3701940A1 (de) * 1986-01-24 1987-07-30 Sundstrand Corp Wahlweise alternative steuerdruckversorgung fuer eine hydraulische verstelleinheit
US5007805A (en) * 1990-07-02 1991-04-16 Caterpillar Inc. Reversible variable displacement hydraulic device
EP1241356A2 (fr) * 2001-03-15 2002-09-18 Teijin Seiki Co., Ltd. Moteur à fluide à pression ayant un régulateur de puissance
DE10358727B3 (de) * 2003-12-15 2005-08-25 Brueninghaus Hydromatik Gmbh Summenleistungsregelvorrichtung

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19949169C2 (de) 1999-10-12 2001-10-11 Brueninghaus Hydromatik Gmbh Verstellvorrichtung

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3169674A (en) * 1962-04-05 1965-02-16 Lund Jens Pump with delivery adjustment
US4157233A (en) * 1975-07-04 1979-06-05 Daikin Kogyo Co., Ltd. Variable delivery hydraulic pump
US4379389A (en) * 1980-09-12 1983-04-12 Caterpillar Tractor Co. Horsepower consumption control for variable displacement pumps
DE3701940A1 (de) * 1986-01-24 1987-07-30 Sundstrand Corp Wahlweise alternative steuerdruckversorgung fuer eine hydraulische verstelleinheit
US5007805A (en) * 1990-07-02 1991-04-16 Caterpillar Inc. Reversible variable displacement hydraulic device
EP1241356A2 (fr) * 2001-03-15 2002-09-18 Teijin Seiki Co., Ltd. Moteur à fluide à pression ayant un régulateur de puissance
DE10358727B3 (de) * 2003-12-15 2005-08-25 Brueninghaus Hydromatik Gmbh Summenleistungsregelvorrichtung

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2011127883A1 (fr) * 2010-04-16 2011-10-20 Robert Bosch Gmbh Plaque de raccordement pour une machine hydrostatique à piston
US9341180B2 (en) 2010-04-16 2016-05-17 Robert Bosch Gmbh Connection plate for a hydrostatic piston machine

Also Published As

Publication number Publication date
DE102007044451A1 (de) 2009-03-19

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