EP1872018B1 - Pilot valve for a hydraulic motor - Google Patents
Pilot valve for a hydraulic motor Download PDFInfo
- Publication number
- EP1872018B1 EP1872018B1 EP05804312A EP05804312A EP1872018B1 EP 1872018 B1 EP1872018 B1 EP 1872018B1 EP 05804312 A EP05804312 A EP 05804312A EP 05804312 A EP05804312 A EP 05804312A EP 1872018 B1 EP1872018 B1 EP 1872018B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- control
- groove
- valve
- bore
- tank
- 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.)
- Not-in-force
Links
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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
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
- F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
- F15B13/0401—Valve members; Fluid interconnections therefor
- F15B13/0402—Valve members; Fluid interconnections therefor for linearly sliding valves, e.g. spool valves
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T137/00—Fluid handling
- Y10T137/8593—Systems
- Y10T137/86493—Multi-way valve unit
- Y10T137/86574—Supply and exhaust
- Y10T137/8667—Reciprocating valve
- Y10T137/86694—Piston valve
- Y10T137/86702—With internal flow passage
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T137/00—Fluid handling
- Y10T137/8593—Systems
- Y10T137/86493—Multi-way valve unit
- Y10T137/86574—Supply and exhaust
- Y10T137/8667—Reciprocating valve
- Y10T137/86694—Piston valve
- Y10T137/8671—With annular passage [e.g., spool]
Definitions
- the invention relates to a control valve for a hydraulic motor according to the preamble of claim 1.
- Hydromotors are used, for example, in cranes for driving hydraulic winches. With such a winch, loads can be lifted and lowered.
- Out DE-A1-39 41 802 is a hydraulic directional control valve is known, which allows a load pressure independent control of a hydraulic motor.
- Out DE-C2-41 36 991 For example, a directional control valve is known that can be used for the same purpose.
- control valve is also in US 2004/0226292 disclosed.
- the invention has for its object to provide a control valve which prevents the previously described torque fluctuations and pulsations without the need for an additional valve assembly, which was previously used to reduce the pulsation or torque fluctuation.
- a hydraulic motor 1 which drives a not shown in detail winch for lifting and lowering a load 2.
- Arrows on the hydraulic motor 1 is shown that the one direction of rotation of the hydraulic motor 1 causes the lowering of the load 2, the opposite direction of rotation of the hydraulic motor 1, the lifting of the load.
- the hydraulic motor 1 is controllable by a control valve 3 designed as a directional control valve with the usual load connections A and B and with a pump connection P and a tank connection T. This corresponds to the known prior art. This also applies to an inserted into the supply line to the hydraulic motor 1 load-holding valve 4, which serves to control the load during lowering.
- a hydraulic motor 1 comes in such applications preferably a Hubverdrängermaschine used, for example, an axial piston machine, as shown in "Dubbel: Taschenbuch for mechanical engineering", Springer-Verlag, 19th edition, on page H5.
- this widespread type of machine has the disadvantage that the flow is not uniform, because this has a considerable degree of non-uniformity ⁇ . It may even follow that at the beginning of the Lifting the load 2, so at very low speed of the hydraulic motor 1, the load 2 drops briefly. This also applies when reducing the speed to stop the load 2. A rational work is hardly possible and there are dangerous moments.
- valve assembly 10 for example, in the corresponding return line from the hydraulic motor 1, as shown in the Fig. 2 is shown.
- a valve assembly 10 which consists of two mutually parallel check valves, namely a biased check valve 11 and a non-biased check valve 12.
- the applicant itself has created in 2001 such a valve assembly.
- the hydraulic oil flowing from the hydraulic motor 1 to the control valve 3 must pass through the valve assembly 10.
- a solution with such an additional valve assembly 10 is complicated to manufacture and expensive and requires space. But the invention is also particularly the object of improving such a solution in terms of functionality.
- Fig. 3 is a view of a spool 20 within a valve body 21 shown, which are the control valve 3 associated.
- the spool 20 is axially displaceable, which is indicated by a double arrow.
- the axial displaceability is effected, as usual in such proportionally operating control valves, by means of at least one drive, wherein electrical, hydraulic or pneumatic drives find uses. Since in the present case, the number and type of drive for the spool 20 does not matter, such a drive has not been shown in the figure.
- transverse bores are present in the valve body 21, which lead up to the longitudinal bore 22.
- a tank connection bore T a first working connection bore A
- a pump connection bore P a second working connection bore B
- a further tank connection bore T two tank connection bores T are shown, which are generally inside the valve body 21 are merged.
- each of the working connection bores A, B must be operationally connectable to the tank connection bore T or to the pump connection bore P in order to enable "lifting" and "sinking" operation.
- the spool 20 has, in order to produce the various connections between the terminal bores T, B, P, A and T, profiled annular grooves. Seen from the left, these are a B-tank groove 23, a B-control groove 24, a pump groove 25, an A-control groove 26 and an A-tank groove 27.
- the principle is common to most directional control valves.
- the relative position of the spool 20 in the longitudinal bore 22 is shown in the Fig. 3 such that the pump connection bore P is completed, that is, there is no connection to one of the adjacent working connection bores A, B. It follows that the hydraulic motor 1 stands still because no hydraulic oil is supplied to it. Shown is the zero or neutral position.
- the control valve 3 shown here for a hydraulic motor 1 ( Fig. 1 )
- an additional narrow auxiliary control groove 28 which is disposed between the B-tank groove 23 and the B-control groove 24.
- At the bottom of this Hilfs marsnut 28 begins a first transverse bore 29 which opens into a longitudinal bore 30, the other end is in communication with a second transverse bore 31.
- This second transverse bore 31 establishes a connection to the B-tank groove 23 and thus to the tank connection bore T.
- a biased check valve 32 is arranged with a biasing spring 33, in such a way that it is to be opened by a higher pressure from the working port bore B ago. The mode of action will be described in more detail later.
- the control edge for controlling the volume flow between the working port bore B and the second tank port bore T is particularly configured.
- the spool 20 On both sides of the auxiliary control groove 28, the spool 20 has short cylindrical sections, namely to the right of a sealing cylinder 35 and to the left of a biasing cylinder 36. To the left, join two frustoconical sections, namely a first control taper portion 37 with a weaker surface inclination and then a second control cone section 38 with a stronger surface inclination.
- Fig. 4 It is shown that one of the working port bore B associated control edge 40 is located in the region of the sealing cylinder 35. Thus exists between the working port bore B and the further left tank connection bore T ( Fig. 3 ) no connection. Because thus also the auxiliary control groove 28 is covered with the transverse bore 29 beginning therein from the control edge 40, the pressure prevailing in the working port bore B does not act in the transverse bore 29 into it. This condition is given when, as in Fig. 3 shown, the connection of the pump port hole P is shut off both the working port hole A and only working port bore B, so that the hydraulic motor 1 (FIG. Fig. 1 ) stands still. Again, the zero or neutral position is shown.
- Fig. 5 is that state shown in which the spool 20 is moved so far to the right against the control edge 40, that now in the working port bore B prevailing pressure can act because of the exposed auxiliary control groove 28 in the transverse bore 29.
- the hydraulic motor 1 ( Fig. 1 ) in function, because at the same time, which from the Fig. 3 can be derived, because of the right shift of the spool 20 hydraulic oil from the pump connection bore P to the first working port bore A and from there to the hydraulic motor 1 flows.
- the hydraulic oil flowing back from the hydraulic motor 1 to the tank at the same time can not now travel directly from the working port bore B to the tank connection bore T located further to the left, because this path is blocked by the sealing action of the pretensioning cylinder 36.
- the hydraulic motor 1 is hydraulically biased, with the result that the uneven startup at low speed is greatly improved in a very simple manner. Accordingly, the degree of non-uniformity ⁇ can not practically work as a non-uniform rotational movement during slow starting. Incidentally, this also applies to the slow speed after a delay from faster running.
- control piston 20 is moved to the right, the greater the flow of hydraulic oil between the control edge 40 and control cone portion 37th That the check valve 32 does not close immediately when the control edge 40 comes into the region of the first control taper portion 37, is because that due to the flow between the control edge 40 and the control cone section 37, an equally high dynamic pressure is created as over the prestressed check valve 32.
- the biasing spring 33 is dimensioned so that the resulting return bias is about 25 bar.
- the surface inclination of the first control cone section 37 is dimensioned approximately such that the angle to the imaginary cylindrical surface of the control spool 20 is approximately 16 °.
- the surface inclination of the second control cone portion 38 is advantageously about 26 °. The dimensions otherwise depend on the size of the control valve 3, ie of its maximum flow. But then it does not require any inventive step to optimize this measure.
- the invention is always applicable when loads are to be lifted in devices with a hydraulic motor.
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Fluid-Pressure Circuits (AREA)
- Valve Device For Special Equipments (AREA)
- Magnetically Actuated Valves (AREA)
- Valve-Gear Or Valve Arrangements (AREA)
- Multiple-Way Valves (AREA)
- Check Valves (AREA)
- Servomotors (AREA)
Abstract
Description
Die Erfindung bezieht sich auf ein Steuerventil für einen Hydromotor gemäß dem Oberbegriff des Anspruchs 1.The invention relates to a control valve for a hydraulic motor according to the preamble of claim 1.
Hydromotoren werden beispielsweise bei Kranen zum Antrieb hydraulischer Winden verwendet. Mit einer solchen Winde lassen sich Lasten heben und senken.Hydromotors are used, for example, in cranes for driving hydraulic winches. With such a winch, loads can be lifted and lowered.
Aus
Aus der Arbeitsweise von Hydromotoren, die meist als Axialkolbenmaschinen, seltener als Radialkolbenmaschinen gestaltet sind, ergibt sich konstruktionsbedingt, dass der Förderstrom nicht gleichmäßig ist, sondern zyklisch schwankt, also pulsiert, wie dies beispielsweise in
Die genannte Aufgabe wird erfindungsgemäß durch die Merkmale des Anspruchs 1 gelöst. Vorteilhafte Weiterbildungen ergeben sich aus den abhängigen Ansprüchen.The above object is achieved by the features of claim 1. Advantageous developments emerge from the dependent claims.
Nachfolgend wird ein Ausführungsbeispiel der Erfindung anhand der Zeichnung näher erläutert.An embodiment of the invention will be explained in more detail with reference to the drawing.
Es zeigen:
-
Fig. 1 ein Schema einer Ansteuerung für einen Hydromotor, -
Fig. 2 eine Ventilbaugruppe als Zusatzaggregat für die Funkion "Heben" gemäß einer Lösung nach dem Stand der Technik, -
Fig. 3 . eine Ansicht eines Steuerschiebers innerhalb eines Ventilkörpers, und -
Fig. 4 bis 7 Ausschnitte der Stellung des Steuerschiebers relativ zu einer Steuerkante.
-
Fig. 1 a diagram of a control for a hydraulic motor, -
Fig. 2 a valve assembly as an accessory for the function "lifting" according to a solution according to the prior art, -
Fig. 3 , a view of a spool within a valve body, and -
Fig. 4 to 7 Cutouts of the position of the spool relative to a control edge.
In der
Im "Heben"-Betrieb strömt das Hydrauliköl vom Pumpenanschluss P des Steuerventils 3 und die A-Leitung durch das sich von selbst öffnende Rückschlagventil des Lasthalteventils 4 zum Hydromotor 1 und treibt diesen an. Gleichzeitig fließt eine identische Menge von Hydrauliköl vom Hydromotor 1 über die B-Leitung durch das Steuerventil 3 zum Tankanschluss T. Die proportionale Flussmengensteuerung erfolgt durch die proportionale Steuerung des Steuerventils 3. Dies ist im hydraulischen Schaltbild des Steuerventils 3 gezeigt.In the "lifting" operation, the hydraulic oil flows from the pump port P of the
Im "Senken"-Betrieb ist die Flussrichtung umgekehrt. Dabei erfolgt die Bewegungssteuerung durch das proportional ansteuerbare Lasthalteventil 4.In "sink" mode, the flow direction is reversed. The movement control is effected by the proportionally controllable load-
Als Hydromotor 1 kommt bei solchen Anwendungsfällen bevorzugt eine Hubverdrängermaschine zum Einsatz, beispielsweise eine Axialkolbenmaschine, wie sie in "Dubbel: Taschenbuch für den Maschinenbau", Springer-Verlag, 19. Auflage, auf der Seite H5, gezeigt ist. Diese weit verbreitete Maschinenbauart hat aber den Nachteil, dass der Förderstrom nicht gleichmäßig ist, weil dieser einen erheblichen Ungleichförmigkeitsgrad δ aufweist. Daraus kann sogar folgen, dass bei Beginn des Anhebens der Last 2, also bei sehr kleiner Drehzahl des Hydromotors 1, die Last 2 kurzzeitig absinkt. Das gilt auch beim Verringern der Drehzahl zum Anhalten der Last 2. Ein rationelles Arbeiten ist so kaum möglich und es ergeben sich Gefahrenmomente.As a hydraulic motor 1 comes in such applications preferably a Hubverdrängermaschine used, for example, an axial piston machine, as shown in "Dubbel: Taschenbuch for mechanical engineering", Springer-Verlag, 19th edition, on page H5. However, this widespread type of machine has the disadvantage that the flow is not uniform, because this has a considerable degree of non-uniformity δ. It may even follow that at the beginning of the Lifting the
Um dieses gravierende Problem wenigstens teilweise zu beheben, hat man versucht, die ungleichförmige Drehbewegung bei Langsamlauf durch die Einbindung einer Ventilbaugruppe 10 zum Beispiel in die entsprechende Rücklaufleitung vom Hydromotor 1 zu verringern, wie dies in der
Eine Lösung mit einer solchen zusätzlichen Ventilbaugruppe 10 ist herstellungsmäßig aufwendig und teuer und benötigt Platz. Der Erfindung liegt aber insbesondere auch noch die Aufgabe zugrunde, eine solche Lösung hinsichtlich Funktionalität zu verbessern.A solution with such an
In der
Wie bei solchen Steuerventilen üblich, sind Querbohrungen im Ventilkörper 21 vorhanden, die bis an die Längsbohrung 22 heranführen. In der
Der Steuerschieber 20 weist, um die verschiedenen Verbindungen zwischen den Anschlussbohrungen T, B, P, A und T herstellen zu können, profilierte Ringnuten auf. Von links her gesehen sind dies eine B-Tank-Nut 23, eine B-Steuernut 24, eine Pumpennut 25, eine A-Steuernut 26 und eine A-Tank-Nut 27. Das Prinzip ist den meisten Wegeventilen gemeinsam.The
Die relative Lage des Steuerschiebers 20 in der Längsbohrung 22 ist bei der Darstellung in der
Erfindungsgemäß weist nun aber das hier gezeigte Steuerventil 3 für einen Hydromotor 1 (
Vorteilhaft ist die Steuerkante zur Steuerung des Volumenstroms zwischen der Arbeitsanschlussbohrung B und der zweiten Tankanschlussbohrung T besonders ausgestaltet. Beidseits der Hilfssteuernut 28 weist der Steuerschieber 20 kurze zylindrische Abschnitte auf, nämlich rechts davon einen Dichtzylinder 35 und links davon einen Vorspannzylinder 36. Nach links schließen sich zwei kegelstumpfförmige Abschnitte an, nämlich ein erster Steuerkegelabschnitt 37 mit einer schwächeren Flächenneigung und dann daran ein zweiter Steuerkegelabschnitt 38 mit einer stärkeren Flächenneigung.Advantageously, the control edge for controlling the volume flow between the working port bore B and the second tank port bore T is particularly configured. On both sides of the
In den
In der
In der
Durch diese Druckerhöhung in der Arbeitsanschlussbohrung B wird der Hydromotor 1 hydraulisch vorgespannt ist, was zur Folge hat, dass der ungleichmäßige Anlauf mit kleiner Drehzahl auf sehr einfache Weise stark verbessert wird. Der Ungleichförmigkeitsgrad δ kann sich entsprechend praktisch nicht als ungleichförmige Drehbewegung beim langsamen Anfahren auswirken. Das gilt im übrigen auch für den Langsamlauf nach einer Verzögerung aus schnellerem Lauf.By this pressure increase in the working port bore B, the hydraulic motor 1 is hydraulically biased, with the result that the uneven startup at low speed is greatly improved in a very simple manner. Accordingly, the degree of non-uniformity δ can not practically work as a non-uniform rotational movement during slow starting. Incidentally, this also applies to the slow speed after a delay from faster running.
In der
Wird der Steuerschieber 20 gegenüber der
Vorteilhaft wird die Vorspannfeder 33 so bemessen, dass die entstehende Rücklaufvorspannung etwa 25 bar beträgt.Advantageously, the biasing
Vorteilhaft wird die Flächenneigung des ersten Steuerkegelabschnitts 37 etwa so bemessen, dass der Winkel zur gedachten Zylinderfläche des Steuerschiebers 20 etwa 16° beträgt. Die Flächenneigung des zweiten Steuerkegelabschnitts 38 beträgt vorteilhaft etwa 26°. Die Maße hängen ansonsten von der Größe des Steuerventils 3 ab, also von dessen maximaler Durchströmung. Es bedarf dann aber keiner erfinderischen Tätigkeit, diese Maß zu optimieren.Advantageously, the surface inclination of the first
Die Erfindung ist immer dann anwendbar, wenn bei Vorrichtungen mit einem Hydromotor Lasten gehoben werden sollen.The invention is always applicable when loads are to be lifted in devices with a hydraulic motor.
Claims (6)
- Control valve (3) for a hydraulic motor (1), by means of which loads (2) can be raised in a device, where the control valve (3) is designed as a directional control valve, in which a control slide (20) is installed in a longitudinal bore (22) of a valve body (21) with freedom to slide back and forth to control the flow of hydraulic oil between two working connection bores (A, B), a pump connection bore (P), and a tank connection bore (T), where the control slide (20) has a B-to-tank groove (23), a B control groove (24), a pump groove (25), an A control groove (26), and possibly an A-to-tank groove (27), where a check valve (32) spring-loaded by a pretensioning spring (33) is located inside the control slide (20),
characterized in that;
the check valve (32) being connected at one end to an auxiliary control groove (28) by way of a first transverse bore (29) and at the other end to the B-to-tank groove (23) by way of a second transverse bore (31),
the check valve (32) can be opened from the side of the working connection bore B; and the auxiliary control groove (28) is located between the B control groove (24) and the B-to-tank groove (23) and is limited on both sides by cylindrical sealing surfaces (35, 36). - Control valve (3) according to Claim 1, characterized in that the pretensioning spring (33) is dimensioned in such a way that it generates a return-flow pretension of approximately 25 bars.
- Control valve (3) according to Claim 2, characterized in that, in the direction toward the B-to-tank groove (23), a first truncated cone-shaped control cone section (37) adjoins the pretensioning cylinder (36) which forms one of the cylindrical surfaces.
- Control valve (3) according to Claim 3, characterized in that the taper of the first control cone section (37) is designed so that the angle to the imaginary surface of the cylinder of the control slide (20) is approximately 16°.
- Control valve (3) according to Claim 4, characterized in that a second truncated cone-shaped control cone section (38) adjoins the first truncated cone-shaped control cone section (37).
- Control valve (3) according to Claim 5, characterized in that the taper of the second control cone section (38) is designed so that the angle to the imaginary surface of the cylinder (20) is approximately 26°.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
CH7072005 | 2005-04-20 | ||
PCT/CH2005/000717 WO2006111031A1 (en) | 2005-04-20 | 2005-12-01 | Pilot valve for a hydraulic motor |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1872018A1 EP1872018A1 (en) | 2008-01-02 |
EP1872018B1 true EP1872018B1 (en) | 2008-08-06 |
Family
ID=35058900
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP05804312A Not-in-force EP1872018B1 (en) | 2005-04-20 | 2005-12-01 | Pilot valve for a hydraulic motor |
Country Status (6)
Country | Link |
---|---|
US (1) | US7921879B2 (en) |
EP (1) | EP1872018B1 (en) |
JP (1) | JP2008537069A (en) |
AT (1) | ATE403807T1 (en) |
DE (1) | DE502005004981D1 (en) |
WO (1) | WO2006111031A1 (en) |
Families Citing this family (11)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP2126373A1 (en) * | 2007-02-22 | 2009-12-02 | Raytheon Sarcos, LLC | First-stage pilot valve |
NO20073463A (en) * | 2007-07-04 | 2008-12-29 | Tool Tech As | Actuator for a pilot for hydraulic control valves |
FI20115418A0 (en) * | 2011-05-03 | 2011-05-03 | Waertsilae Finland Oy | FUEL INJECTION UNIT AND SYSTEM |
DE102011087546A1 (en) | 2011-08-09 | 2013-02-14 | Robert Bosch Gmbh | Slide valve with a valve slide which can be acted upon by an actuator |
WO2013090728A2 (en) * | 2011-12-15 | 2013-06-20 | Eaton Corporation | Flow directing spool for valve |
CN103644158B (en) * | 2013-12-26 | 2015-12-02 | 太重集团榆次液压工业有限公司 | Electromagnetic pilot sliding valve style hydraulicdirectional control valve |
JP2015169212A (en) * | 2014-03-04 | 2015-09-28 | 株式会社デンソー | fluid control valve |
US10207905B2 (en) | 2015-02-05 | 2019-02-19 | Schlumberger Technology Corporation | Control system for winch and capstan |
DE102018102397A1 (en) | 2018-02-02 | 2019-08-08 | J.D. Neuhaus Holding Gmbh & Co. Kg | Control valve arrangement for indirect pneumatic control |
EP3660332B1 (en) * | 2018-11-27 | 2023-05-17 | Hamilton Sundstrand Corporation | Servo valve |
EP3715644B1 (en) * | 2019-03-29 | 2023-11-08 | Hamilton Sundstrand Corporation | Spool servo valve |
Family Cites Families (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3265088A (en) | 1963-10-11 | 1966-08-09 | Commercial Shearing | Control valves of the series type |
US3738379A (en) | 1971-08-02 | 1973-06-12 | Koehring Co | Control valve with semi-automatically indexed valve element |
DE2807464C2 (en) * | 1978-02-22 | 1982-11-25 | Zahnradfabrik Friedrichshafen Ag, 7990 Friedrichshafen | Power steering |
DE3016533A1 (en) * | 1980-04-29 | 1981-11-05 | Linde Ag, 6200 Wiesbaden | SLIDE VALVE |
JPH0419220Y2 (en) * | 1986-05-19 | 1992-04-30 | ||
DE3941802A1 (en) | 1989-12-19 | 1991-06-20 | Bosch Gmbh Robert | Hydraulic directional control valve for load sensing - incorporated method of preventing leakages in neutral position |
DE4136991C2 (en) | 1991-11-11 | 2000-11-02 | Bosch Gmbh Robert | Hydraulic directional valve |
US6868672B2 (en) * | 2003-05-13 | 2005-03-22 | Sauer-Danfoss, Inc. | Method of controlling a swinging boom and apparatus for controlling the same |
FR2857704B1 (en) * | 2003-07-16 | 2007-12-28 | Bosch Rexroth Dsi Sas | HYDRAULIC DISTRIBUTOR WITH TORQUE SLOTS |
DE10357471A1 (en) * | 2003-12-09 | 2005-07-07 | Bosch Rexroth Ag | Hydraulic control arrangement |
-
2005
- 2005-12-01 AT AT05804312T patent/ATE403807T1/en not_active IP Right Cessation
- 2005-12-01 EP EP05804312A patent/EP1872018B1/en not_active Not-in-force
- 2005-12-01 WO PCT/CH2005/000717 patent/WO2006111031A1/en active IP Right Grant
- 2005-12-01 US US11/918,688 patent/US7921879B2/en not_active Expired - Fee Related
- 2005-12-01 DE DE200550004981 patent/DE502005004981D1/en active Active
- 2005-12-01 JP JP2008506896A patent/JP2008537069A/en active Pending
Also Published As
Publication number | Publication date |
---|---|
US20090078112A1 (en) | 2009-03-26 |
WO2006111031A1 (en) | 2006-10-26 |
DE502005004981D1 (en) | 2008-09-18 |
ATE403807T1 (en) | 2008-08-15 |
JP2008537069A (en) | 2008-09-11 |
US7921879B2 (en) | 2011-04-12 |
EP1872018A1 (en) | 2008-01-02 |
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