WO2014127955A1 - Ensemble hydraulique - Google Patents

Ensemble hydraulique Download PDF

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Publication number
WO2014127955A1
WO2014127955A1 PCT/EP2014/051371 EP2014051371W WO2014127955A1 WO 2014127955 A1 WO2014127955 A1 WO 2014127955A1 EP 2014051371 W EP2014051371 W EP 2014051371W WO 2014127955 A1 WO2014127955 A1 WO 2014127955A1
Authority
WO
WIPO (PCT)
Prior art keywords
hydraulic
unit
piston
cylinder
fluid
Prior art date
Application number
PCT/EP2014/051371
Other languages
German (de)
English (en)
Inventor
Josef Büttner
Armin Christ
Original Assignee
Saf-Holland 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 Saf-Holland Gmbh filed Critical Saf-Holland Gmbh
Publication of WO2014127955A1 publication Critical patent/WO2014127955A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B1/00—Installations or systems with accumulators; Supply reservoir or sump assemblies
    • F15B1/02—Installations or systems with accumulators
    • F15B1/025—Installations or systems with accumulators used for thermal compensation, e.g. to collect expanded fluid and to return it to the system as the system fluid cools down
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
    • F15B21/04—Special measures taken in connection with the properties of the fluid
    • F15B21/045—Compensating for variations in viscosity or temperature
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
    • F15B15/08—Characterised by the construction of the motor unit
    • F15B15/14—Characterised by the construction of the motor unit of the straight-cylinder type
    • F15B15/1423—Component parts; Constructional details
    • F15B15/1433—End caps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
    • F15B15/08—Characterised by the construction of the motor unit
    • F15B15/14—Characterised by the construction of the motor unit of the straight-cylinder type
    • F15B15/1423—Component parts; Constructional details
    • F15B15/1447—Pistons; Piston to piston rod assemblies
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
    • F15B15/08—Characterised by the construction of the motor unit
    • F15B15/14—Characterised by the construction of the motor unit of the straight-cylinder type
    • F15B15/1423—Component parts; Constructional details
    • F15B15/1457—Piston rods

Definitions

  • the present invention relates to a hydraulic unit, particularly preferably a hydraulic unit for use in commercial vehicles, according to independent claim 1.
  • Hydraulic units are known from the prior art for a long time. They serve to convert compressive forces in a hydraulic fluid into translational movements or forces. Usually, a piston is displaced relative to a cylinder by targeted application of pressure in the hydraulic fluid in the cylinder. In addition to the arrangement of the piston and cylinder such hydraulic units comprise a mostly closed circuit of hydraulic fluid or hydraulic fluid. During operation of the hydraulic unit, preferably on a commercial vehicle, this hydraulic fluid is sometimes exposed to temperature fluctuations in which it can greatly expand or contract strongly. Combined with the technically most required approximate incompressibility of the hydraulic fluid, high pressures can occur in this way, which under certain circumstances can cause a leakage of the hydraulic fluid or even damage to hydraulic lines or individual assemblies of the hydraulic unit.
  • the object of the present invention is to provide a hydraulic unit which reduces the space requirement of a hydraulic system, reduces the installation effort and at the same time protects the hydraulic system against excessively high or too low pressures and thus against damage.
  • the hydraulic unit comprises a cylinder and a piston unit, wherein the piston unit extends at least partially into a fluid space enclosed by the cylinder and is displaceable relative to the cylinder, wherein a hydraulic fluid is provided in the fluid space, wherein in the cylinder and / or the piston unit a compensation chamber is provided with the
  • Hydraulic fluid is in fluid-conducting connection and wherein a return means is provided in the expansion chamber.
  • the hydraulic unit essentially comprises the two assemblies cylinder and piston unit, wherein the cylinder is a substantially tubular body, in the cavity of which the piston unit is arranged to be displaceable.
  • the hydraulic unit is, for example, a hydraulically operated steering cylinder of a steering system of a motor vehicle, particularly preferably a commercial vehicle.
  • the cylinder can have one or a plurality of openings in the lateral surface, through which a hydraulic fluid can be pumped into or out of the cylinder.
  • a fluid space is formed by the cylinder, in which a hydraulic fluid is provided.
  • the hydraulic fluid preferably fills the interior of the cylinder and thereby surrounds the piston unit, which is also located in the interior of the cylinder.
  • the hydraulic fluid is preferably a hydraulic oil having properties known in the art.
  • the piston unit has a piston rod and a piston, wherein the piston is designed such that its outer edge or outer surface, particularly preferably corresponds to the inner surface of the fluid space of the cylinder, wherein the piston preferably the fluid space of the cylinder in two Divided areas, which are sealed by the piston against each other.
  • each of these two regions of the fluid space which are separated from each other by the piston of the piston unit, has a connection or recess with corresponding connection geometries for connection to a pipeline system, through which hydraulic fluid is pumped into or out of the respective region of the fluid chamber can be transported out.
  • the functional principle of the hydraulic unit preferably corresponds to the principle of a synchronizing cylinder, as is generally known in the prior art.
  • the present invention may also preferably be used in differential cylinders which are also presumed to be of the prior art.
  • a compensation chamber in which the hydraulic fluid can flow when the total pressure of the hydraulic fluid exceeds a permissible limit.
  • a return means is arranged, which opposes the inflow of the hydraulic fluid, a force or a counteracting pressure or surface pressure.
  • the return means is a compressible gas, a silicone foam or a combination of a piston with an elastically deformable return element, such as a spring.
  • the compensation chamber is arranged within a space defined by the cylinder and the piston unit. In other words, the compensation space is provided either in the cylinder or in the piston unit.
  • the space requirement of the hydraulic unit can be significantly reduced.
  • the sensitivity to damage as they can occur especially in the range of a chassis of a commercial vehicle by parts whirled up, minimized by the compact design with few external components.
  • the appropriate return means ie, in particular by the compressibility or deformability of the material and by its volume fraction based on the total volume of the hydraulic fluid in the hydraulic unit, the desired behavior of the hydraulic unit can be adjusted with increasing pressure in the hydraulic fluid.
  • Further adjustment such as valves or pumping systems can be connected to the expansion chamber, by means of which the force applied by the return means force or the pressure applied by the return means pressure is adjustable, which counteracts the inflow of hydraulic fluid.
  • the compensation chamber is arranged within a space defined by the cylinder.
  • the volume defined by the cylinder is referred to as the volume defined by the component cylinder, in particular by its outer surfaces, wherein the compensation chamber should preferably be arranged within this volume.
  • the compensation chamber is arranged in the region of the cover of the cylinder, which are attributed to the space spanned by the cylinder. It is particularly preferred that the space defined by the cylinder essentially corresponds to a mathematical cylinder. In other words, no bulges are provided on the cylinder for the compensation chamber, wherein the particularly compact design of the cylinder or the hydraulic unit is achieved.
  • the compensation chamber communicates with the fluid space via a channel, the channel preferably being arranged below the return means.
  • the channel below the return means in this context, the arrangement of the channel in case of proper installation or proper arrangement of the hydraulic unit on the motor vehicle in the direction of gravity referred to understood below the return means.
  • the return means is a gas and can be expected that this is lighter than the hydraulic fluid and by static buoyancy upwards, ie opposite to the direction of gravity, rises in the hydraulic fluid
  • the channel below the return means is arranged to prevent leakage of the return means in the fluid space.
  • the correct installation position of the cylinder or the hydraulic unit usually results from the arrangement of the supply and discharge nozzles of the hydraulic fluid on the cylinder of the hydraulic unit, or by corresponding force supply and discharge geometries, such as eyelets or bearing eyes on the piston unit , Further preferably, it may be that in the channel, a valve is arranged, wherein the valve is designed to prevent an inflow of the hydraulic fluid into the expansion chamber to an overpressure of the hydraulic fluid.
  • the preferred provided valve is in other words a kind of pressure relief valve, which only when reaching a certain pressure difference across the valve in an open position at which hydraulic fluid can flow through the valve and thus through the channel from the fluid chamber into the expansion chamber.
  • an inflow and outflow of hydraulic fluid into the expansion chamber is prevented when in the hydraulic unit there is only a relatively small overpressure of the hydraulic fluid, which does not pose any danger to the hydraulic unit or the hydraulic system.
  • a change in the operating characteristic, or the response of the hydraulic unit to applied pressure values for controlling the hydraulic unit is avoided.
  • the return means engage only when threatening a risk of overpressure in the hydraulic unit or in the hydraulic system of the hydraulic unit leave, as this results in an unwanted cushioning or damping of the reaction of the hydraulic unit to applied pressure differences.
  • the limit value of the pressure of the hydraulic fluid starting from which hydraulic fluid flows into the compensation chamber, a 1, 2 to 2 times, more preferably a 1, 4 to 1, 7 times the usual operating pressure of the hydraulic fluid under standard operating conditions.
  • the valve is adjustable, so that the concrete limit over pressure, from which the valve switches, depending on the needs of the user can be adjusted.
  • the pressure difference across the valve is preferably considered.
  • two limit overpressure values are provided, a first, which must be present, so that the inflow of the hydraulic fluid into the compensation chamber is possible, and a second, from which the hydraulic fluid flows out of the compensation chamber.
  • a displaceable balance piston is provided in the compensation space between the return means and the hydraulic fluid, wherein the balance piston forces between the hydraulic fluid and the return means über-. wearing.
  • the compensating piston is preferably arranged in a sealed manner in the compensation chamber, this displaceable and forms a barrier between the region of the compensation chamber, which can be filled with hydraulic fluid, or filled and the region of the compensation chamber, in which the return means is arranged. If a certain volume of hydraulic fluid flows into the compensation chamber at a high pressure of the hydraulic fluid, this fluid displaces the compensation piston in the direction of the return means, wherein the return means is preferably deformed or compressed or displaced.
  • a membrane is provided which prevents the return means from emerging from the expansion chamber.
  • a film, a rubber or a similarly elastically deformable material may preferably be provided as membrane material.
  • the membrane is formed as a bubble or surrounds the return means, which may be for example a gas or a deformable foam completely.
  • the membrane is provided as a separating layer in the compensation chamber and prevents the return agent from entering the channel or even the fluid space of the cylinder.
  • the return means occupies a volume which is in a ratio of 0.001-0.05, preferably 0.001-0.02 and more preferably about 0.002-0.008, to the volume of the hydraulic fluid.
  • the standard operating state in this context is the state of the hydraulic unit, or of the entire hydraulic system at normal temperature, ie, preferably 20 ° C outside temperature and a state of the hydraulic unit, in which no force from the piston or the piston unit is transmitted.
  • the hydraulic unit is preferably filled with the normal or operational quantity of hydraulic fluid, and in this state an idling pressure prevails in the hydraulic fluid. It is understood that when the total pressure in the hydraulic fluid and thus in the hydraulic unit increases, the volume fraction of the return means by the
  • the preferred ratios of the volume of the return means compared to the volume of the hydraulic fluid are particularly preferably used on the one hand to provide sufficient compensation for overpressure and on the other hand not to influence the operating characteristics of the hydraulic unit by excessive amounts of deformable or compressible media too strong. It has been shown that the lower limit of the volume ratio of 0.001 for most known hydraulic fluids offers a sufficient compensation possibility in the usual temperature fluctuations during operation. The upper limit of the volume ratio of 0.005 makes it possible on hydraulic units, which are subject to severe temperature fluctuations, on the one hand, to have the operating characteristics, i. that is, to not unduly bias or distort the hydraulic response while providing the required large hydraulic fluid compensation spaces at high pressures.
  • a plurality of compensation spaces are provided on the piston unit and / or on the cylinder.
  • compensation chambers may be distributed both on the piston unit and on the cylinder.
  • the material weakening caused by the introduction of a compensation chamber in the form of a chamber in the wall or in supporting structures of the cylinder or piston unit and thus the strength weakening on the cylinder as well as on the piston unit can be minimized.
  • a quantity of the return means adapted to the respective size of the compensation chamber is arranged in each of the compensation chambers.
  • the return means occupy a total volume in the equalization compartments which is in a ratio of 0.001-0.05, preferably 0.001-0.02 and more preferably about 0.002-0.008, to the volume of the hydraulic fluid. Similar to the preferred single compensation space described above, it is preferred that the total volume of the return means, which is distributed over a plurality of equalization spaces, does not exceed or fall below the corresponding volume ratio of 0.001-0.05. It can thus be ensured that the advantages described above for the operating characteristic and for the safety against overpressure, which can be achieved by a certain volume of the return means relative to the total volume of the hydraulic fluid in the hydraulic unit.
  • the volume of the hydraulic fluid is thereby preferably defined as the total volume of the hydraulic fluid in the entire hydraulic system, ie, not only in the hydraulic unit, but also in all adjacently arranged line or pump sections, since an expansion of the hydraulic fluid ultimately in all areas of the hydraulic fluid system is expected and should be compensated by the compression of the return means.
  • the compensation chamber is arranged in the Kolbenein- unit.
  • a compensation space in addition to the possibilities available in the cylinder, and to also use the spaces available in the piston unit, preferably one or a plurality of compensation spaces can be arranged in the piston unit.
  • the piston rod of the piston unit is designed as a hollow body, in which the hydraulic fluid in the presence of a corresponding overpressure on or can flow out of this again upon reaching the standard operating state. It is understood that when arranging compensation spaces in the piston unit whose strength or required wall thicknesses may not be unduly reduced.
  • the piston unit has a piston rod, which is at least partially hollow body-shaped, wherein the compensation chamber is arranged in the piston rod.
  • the piston rod is preferably made of two parts formed, wherein the compensation space is arranged between the sub-elements.
  • the sub-elements of the piston rod are preferably screwed to the piston rod, wherein a cavity remains in the region of the screw, which is used as a compensation chamber. It is advantageous here that the size of the compensation chamber can be changed by adjusting the screwing position of the two partial elements and thus the available volume can be adapted. It is thus possible to adapt the hydraulic unit to different operating conditions.
  • the compensation chamber may be a chamber in a cover of the cylinder.
  • An advantage of the arrangement of the compensation chamber in the cover of the cylinder it may be that this cover of the cylinder is easily accessible from the outside by the user and so adjustment means can be provided, via which the behavior, in particular the inlet and outflow, preferably provided valves or corresponding values of the return means from the outside by the user adjustable or adjustable even during operation of the hydraulic unit.
  • a compensation chamber arranged in the cover of the cylinder can have an additional overpressure passage, through which the hydraulic fluid can be discharged into the environment when a certain critical pressure is exceeded, in order to prevent destruction of the hydraulic unit in the most extreme emergency.
  • the piston unit is displaceable along a piston axis relative to the cylinder, wherein the piston unit and the fluid chamber are rotationally symmetrical about the piston axis.
  • Fig. 5 is a sectional view of a preferred embodiment of the hydraulic unit according to the invention.
  • All embodiments shown in the figures have in common that a preferably cylinder-shaped cylinder 2 and a piston unit 4 is provided, which together form the hydraulic unit 1.
  • the piston unit 4 is guided in the cylinder 2 or arranged to be displaceable.
  • the preferred application of the hydraulic unit 1 is a steering cylinder of a motor vehicle steering system. Particularly preferably, the hydraulic unit 1 is used in a commercial vehicle.
  • the preferred embodiment of the hydraulic unit 1 shown in FIG. 1 also has two covers 24, which are provided on the cylinder 2, preferably at its distal ends on the right and left in the figure.
  • the cover 24 may preferably be screwed, welded or soldered. In the preferred embodiment shown in FIG.
  • a compensation space 8 is provided in one of the covers 24, which is in fluid-conducting connection via a channel 82 with the fluid space 22 formed by the cylinder 2.
  • the compensation chamber 8 is particularly preferably introduced as a chamber or recess in the lid 24.
  • a return means 10 is arranged, wherein the return means 10 in the embodiment shown is a preferred gas bubble.
  • the compensation chamber 8 is replaced by the piston Stem 42 of the piston unit 4 penetrated, whereby the compensation chamber 8 receives an annular or annular space geometry.
  • the return means 10 is preferably a compressible gas and, in a standard operating state of the hydraulic unit 1, preferably assumes a volume V k which is in a preferred ratio to the volume V 1 of the hydraulic fluid 6.
  • the figures each show only the part of the volume V, the hydraulic fluid 6 which is located in the hydraulic unit 1.
  • the piston unit 4 has a piston 44, which preferably divides the fluid space 22 into two separate areas.
  • the compensation chamber 8 is arranged in the piston unit 4.
  • the compensation chamber 8 is provided in the piston rod 42 of the piston unit 4 and is fluid-conductively connected to the fluid space 22 via a channel 82.
  • a membrane 12 is provided which preferably surrounds the return means 10 and thus prevents it from emerging from the compensation space 8.
  • the diaphragm 12 is provided with the return means 10 surrounding a hydraulic fluid 6, which is preferably a substantially incompressible medium.
  • the piston rod 42 is formed from two sub-elements, wherein the first sub-element is screwed into the second. As shown in FIG. 1 and FIG.
  • a gap which can be used as a compensation chamber 8 preferably remains in the joining region of the two subelements.
  • the size or the volume of the compensation chamber 8 can be changed and adapted to specific operating conditions of the hydraulic unit 1 by screwing in or unscrewing one partial element into the other. It is understood that this compensation chamber 8 arranged in the piston unit 4 can also be used in the execution spaces shown in FIGS. 1 and 3 -5.
  • FIG 3 shows a preferred embodiment of the hydraulic unit 1 according to the invention, wherein the compensation chamber 8 is preferably arranged in the piston 44 of the piston unit 4 and is fluid-conductively connected via a channel 82 to the fluid space 22. is bound.
  • a compensation piston 84 is arranged in the compensation chamber 8, which spatially separates the return means 10 arranged in the compensation chamber 8 from the hydraulic fluid 6 which has flowed into the compensation chamber 8.
  • the compensating piston 84 is in particular preferably displaceable within the compensating space 8, in the embodiment shown in the figure, that is to say preferably displaced from the right to the left in the horizontal direction.
  • annular-shaped compensation chamber 8 is preferably an annular trained compensating piston 84 is provided with corresponding seals, which slide on the inner walls of the compensation chamber 8.
  • the piston 44 must be divided into two, because otherwise the balance piston 84 is not introduced into the expansion chamber 8.
  • the compensating piston 84 is therefore displaced more to the left or more to the right and the restoring means 10 is compressed less or more.
  • the return means 10 is formed as a spring, which opposes a displacement of the balance piston 84 in the figure to the right a restoring force.
  • FIG. 4 shows a further preferred embodiment of the hydraulic unit 1 according to the invention, wherein the compensation chamber 8 is arranged in the piston rod 42 of the piston unit 4 and, wherein in the compensation chamber 8 a compensating piston 84 is arranged displaceably.
  • a return means 10 is in this preferred embodiment, a spring, preferably a coil spring, arranged in the expansion chamber 8, which transmits a restoring force on the balance piston 84 and thus seeks to shift such that an inflow of hydraulic fluid 6 is hindered in the expansion chamber 8. Since no gaseous return means 10 is arranged in the compensation chamber 8 in this preferred embodiment, the channel 82, via which the compensation chamber 8 is fluid-conductively connected to the fluid chamber 22, can also be arranged above the return means 10.
  • the compensating piston 84 prevents a mixing of hydraulic fluid 6 with the return adjusting means 10 and a leakage of the return means 10 from the compensation chamber 8 in the fluid space 22nd
  • FIG. 5 shows a further preferred embodiment of the hydraulic unit 1 according to the invention, wherein a plurality of compensation chambers 8 are provided.
  • a plurality of compensation chambers 8 are provided.
  • at least one compensation chamber 8 is provided both in the cylinder 2 and in the piston unit 4.
  • a compensation chamber 8 is arranged in the piston rod 42 of the piston unit 4, while it may also be preferable to arrange a further compensation chamber 8 in the piston 44 (not shown).
  • a return means 10 is arranged in each compensation chamber 8, wherein in the embodiment shown, the return means 10 are designed as gas bubbles, which are each completely enveloped by a membrane.
  • the membrane 12 preferably separates the return means 10 from the surrounding hydraulic fluid 6 and thus particularly preferably prevents leakage of the return means 10 from the respective compensation chamber 8.
  • one or more valves 86 are provided which are each arranged in a channel 82 and serve to control the inflow and outflow of hydraulic fluid 6 into the expansion chamber 8. It may be particularly preferred that a certain pressure difference must be applied to the valve 86, so that the valve is in an open position and hydraulic fluid 6 through the channel 82 in the compensation chamber 8 on or can flow out of this. As shown on the left cover 24 of the cylinder 2, it may be preferred that two channels 82 are provided, one of which is for inflow of the hydraulic fluid 6 and one for the outflow of the hydraulic fluid 6, both in one direction only opening valve 86 are equipped.
  • the compensation chambers 8 are equipped with a valve 86, but that individual, such.
  • the compensation chamber shown in the figure 8 right through an open channel 82 are fluidly connected to the fluid chamber 22 of the cylinder 2.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Actuator (AREA)

Abstract

La présente invention concerne un ensemble hydraulique comprenant un cylindre et un ensemble piston. L'ensemble piston s'étend au moins par endroits dans un espace fluidique délimité par le cylindre et il peut se déplacer par rapport audit cylindre, l'espace fluidique contenant un fluide hydraulique. Le cylindre et/ou l'ensemble piston comporte une chambre de compensation qui est en communication fluidique avec l'espace fluidique et qui contient un moyen de rappel.
PCT/EP2014/051371 2013-02-21 2014-01-24 Ensemble hydraulique WO2014127955A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102013202802.4A DE102013202802A1 (de) 2013-02-21 2013-02-21 Hydraulikeinheit
DE102013202802.4 2013-02-21

Publications (1)

Publication Number Publication Date
WO2014127955A1 true WO2014127955A1 (fr) 2014-08-28

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PCT/EP2014/051371 WO2014127955A1 (fr) 2013-02-21 2014-01-24 Ensemble hydraulique

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DE (1) DE102013202802A1 (fr)
WO (1) WO2014127955A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3722620A1 (fr) * 2019-04-12 2020-10-14 Robert Bosch GmbH Cylindre de serrage sous-marin à actionnement hydraulique en puissance
CN113027853A (zh) * 2021-02-01 2021-06-25 北京航空航天大学 轻量化一体式活塞杆结构

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ITUB20152856A1 (it) * 2015-08-04 2017-02-04 Antonioni Hydraulic Solutions S R L Attuatore idraulico, particolarmente del tipo ammortizzato e/o smorzatore.
RU2610372C1 (ru) * 2015-10-15 2017-02-09 Закрытое акционерное общество "Технологический институт горно-обогатительного машиностроения" (ЗАО "ТИГОМ") Гидроцилиндр двустороннего действия с двусторонним штоком
DE102016117818B4 (de) 2016-09-21 2018-05-03 Saf-Holland Gmbh Achssystem
PL238320B1 (pl) * 2018-04-10 2021-08-09 Politechnika Lodzka Siłownik pneumatyczny
PL239757B1 (pl) * 2018-04-10 2022-01-03 Politechnika Lodzka Silownik pneumatyczny
CN112682387B (zh) * 2021-01-14 2023-05-09 山东浩睿智能科技有限公司 一种自动回中转向油缸
DE102021114814B4 (de) 2021-06-09 2024-04-18 Hoerbiger Automotive Komfortsysteme Gmbh Linear-Aktuator

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3893377A (en) * 1972-10-17 1975-07-08 Philips Corp Hydraulic servomotor
US6035634A (en) * 1999-02-09 2000-03-14 Latch-Tool Development Co. Llc Compact, resistance regulated, multiple output hydraulic tool and seal valve arrangement
DE10218145A1 (de) * 2001-04-23 2002-10-31 Valeo Elektrohydraulische Betätigungseinrichtung, insbesondere für die Betätigung einer Kraftfahrzeugkupplung
JP2009047237A (ja) * 2007-08-20 2009-03-05 Sumitomo Precision Prod Co Ltd アクチュエータシステム

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3893377A (en) * 1972-10-17 1975-07-08 Philips Corp Hydraulic servomotor
US6035634A (en) * 1999-02-09 2000-03-14 Latch-Tool Development Co. Llc Compact, resistance regulated, multiple output hydraulic tool and seal valve arrangement
DE10218145A1 (de) * 2001-04-23 2002-10-31 Valeo Elektrohydraulische Betätigungseinrichtung, insbesondere für die Betätigung einer Kraftfahrzeugkupplung
JP2009047237A (ja) * 2007-08-20 2009-03-05 Sumitomo Precision Prod Co Ltd アクチュエータシステム

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3722620A1 (fr) * 2019-04-12 2020-10-14 Robert Bosch GmbH Cylindre de serrage sous-marin à actionnement hydraulique en puissance
CN113027853A (zh) * 2021-02-01 2021-06-25 北京航空航天大学 轻量化一体式活塞杆结构

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