EP1481168B1 - Hydraulisches ventilaggregat für mehrere funktionen - Google Patents

Hydraulisches ventilaggregat für mehrere funktionen Download PDF

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Publication number
EP1481168B1
EP1481168B1 EP20030701411 EP03701411A EP1481168B1 EP 1481168 B1 EP1481168 B1 EP 1481168B1 EP 20030701411 EP20030701411 EP 20030701411 EP 03701411 A EP03701411 A EP 03701411A EP 1481168 B1 EP1481168 B1 EP 1481168B1
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EP
European Patent Office
Prior art keywords
operator
valve
hydraulic
port
assembly
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.)
Expired - Lifetime
Application number
EP20030701411
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English (en)
French (fr)
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EP1481168A1 (de
Inventor
Luciano Mondani
Mark Dodd
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.)
Lift Technologies Inc Canada
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Lift Technologies Inc Canada
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Filing date
Publication date
Priority claimed from US10/120,789 external-priority patent/US6782910B2/en
Application filed by Lift Technologies Inc Canada filed Critical Lift Technologies Inc Canada
Publication of EP1481168A1 publication Critical patent/EP1481168A1/de
Application granted granted Critical
Publication of EP1481168B1 publication Critical patent/EP1481168B1/de
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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66F—HOISTING, LIFTING, HAULING OR PUSHING, NOT OTHERWISE PROVIDED FOR, e.g. DEVICES WHICH APPLY A LIFTING OR PUSHING FORCE DIRECTLY TO THE SURFACE OF A LOAD
    • B66F9/00—Devices for lifting or lowering bulky or heavy goods for loading or unloading purposes
    • B66F9/06—Devices for lifting or lowering bulky or heavy goods for loading or unloading purposes movable, with their loads, on wheels or the like, e.g. fork-lift trucks
    • B66F9/075—Constructional features or details
    • B66F9/12—Platforms; Forks; Other load supporting or gripping members
    • B66F9/14—Platforms; Forks; Other load supporting or gripping members laterally movable, e.g. swingable, for slewing or transverse movements
    • B66F9/142—Movements of forks either individually or relative to each other
    • B66F9/143—Movements of forks relative to each other - symmetric
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66F—HOISTING, LIFTING, HAULING OR PUSHING, NOT OTHERWISE PROVIDED FOR, e.g. DEVICES WHICH APPLY A LIFTING OR PUSHING FORCE DIRECTLY TO THE SURFACE OF A LOAD
    • B66F9/00—Devices for lifting or lowering bulky or heavy goods for loading or unloading purposes
    • B66F9/06—Devices for lifting or lowering bulky or heavy goods for loading or unloading purposes movable, with their loads, on wheels or the like, e.g. fork-lift trucks
    • B66F9/075—Constructional features or details
    • B66F9/12—Platforms; Forks; Other load supporting or gripping members
    • B66F9/14—Platforms; Forks; Other load supporting or gripping members laterally movable, e.g. swingable, for slewing or transverse movements
    • B66F9/147—Whole unit including fork support moves relative to mast
    • B66F9/148—Whole unit including fork support moves sideways
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66F—HOISTING, LIFTING, HAULING OR PUSHING, NOT OTHERWISE PROVIDED FOR, e.g. DEVICES WHICH APPLY A LIFTING OR PUSHING FORCE DIRECTLY TO THE SURFACE OF A LOAD
    • B66F9/00—Devices for lifting or lowering bulky or heavy goods for loading or unloading purposes
    • B66F9/06—Devices for lifting or lowering bulky or heavy goods for loading or unloading purposes movable, with their loads, on wheels or the like, e.g. fork-lift trucks
    • B66F9/075—Constructional features or details
    • B66F9/20—Means for actuating or controlling masts, platforms, or forks
    • B66F9/22—Hydraulic devices or systems
    • 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
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • F15B11/20—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors controlling several interacting or sequentially-operating members
    • 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
    • F15B13/06—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with two or more servomotors
    • F15B13/07—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with two or more servomotors in distinct sequence
    • 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
    • Y10T137/2496—Self-proportioning or correlating systems
    • Y10T137/2544—Supply and exhaust type
    • Y10T137/2554—Reversing or 4-way valve systems
    • 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
    • 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 is related to hydraulic systems, and in particular, to a multi-function hydraulic valve assembly.
  • hydraulic systems for moving or lifting loads.
  • such systems utilize hydraulic fluid under pressure to drive hydraulic operators, such as piston/cylinder arrangements.
  • a piece of machinery, such as a hoist or a truck may require several hydraulic operators to move the load in different ways.
  • the various hydraulic operators are each controlled by a lever located in the cab of the machine or vehicle.
  • One example where hydraulic systems are used in this way are lift trucks.
  • Lift trucks are vehicles which are used to pick up and move loads from place to place.
  • a conventional lift truck includes a carriage which supports a pair of forks. The forks are maneuvered into place by the lift truck operator and are used to pick up the load.
  • the carriage rides vertically in a mast, which also supports the carriage. In addition the mast may be tilted backward to facilitate stabilizing the load on the forks.
  • Two separate hydraulic operators are used to move the carriage vertically and to tilt the mast.
  • a side shift assembly which facilitates aligning the spaced pair of forks with the load.
  • side shifting is used io describe the concept of shifting the forks as a spaced pair either left or right of the vehicle center line. This function provides the operator with a greater margin for error when aligning the vehicle with the load.
  • a hydraulic operator such as a piston/cylinder arrangement is typically used by the side shifting assembly to move a frame to which the forks are secured.
  • a fork positioning assembly Another attachment to enhance the capability of a lift truck is a fork positioning assembly.
  • the term fork positioning is used to describe the concept of changing the relative spacing between the forks to accommodate loads of different widths.
  • a hydraulic operator such as a piston/cylinder arrangement is used in the fork positioning assembly to move the forks.
  • a cab of a conventional lift truck provides three levers to operate three hydraulic operators. Accordingly, if a user requires four hydraulic operators, such as, for example, by installing a fork positioning attachment, an additional lever must be installed to operate the fork positioning attachment.
  • prior art systems such as US-A-5 139 385 permit operation of two separate hydraulic operators with a single lever on a lift truck. These systems utilize an electrical circuit to toggle between the two hydraulic operators. Prior to moving the lever which actuates the hydraulic system, the user would activate the electrical switch to select the appropriate hydraulic operator. This system adds expense and complexity to the design of the lift truck. In addition, electrical cables must be provided and extended over the lift truck mast.
  • FR2720123 discloses an automated hydraulic control for use in ploughs.
  • the present invention relates to a hydraulic valve assembly as set out in claim 1.
  • Figure 1 is a schematic of a hydraulic system for a lift truck
  • Figure 2 is a perspective view of a valve assembly according to a preferred embodiment of the present invention.
  • Figure 3 is a cross-sectional view of a valve block for the preferred embodiment of Figure 2 ;
  • Figure 4 is a perspective view of a selection valve for the preferred embodiment of Figure 2 ;
  • Figure 5A is a cross-sectional view of the preferred embodiment of Figure 2 in a first position showing fluid flow in one direction;
  • Figure 5B is a cross-sectional view of the preferred embodiment in the first position as shown in Figure 5A , but showing fluid flow in an opposite direction;
  • Figure 5C is a cross-sectional view of the preferred embodiment of Figure 2 in a second position showing fluid flow in one direction;
  • Figure 5D is a cross-sectional view of the preferred embodiment in the second position, as shown in Figure 5C , but showing fluid flow in the opposite direction;
  • Figure 6 is a schematic view showing the preferred embodiment of Figure 2 connected to a side shifter and fork positioner.
  • FIG. 1 shows a hydraulic system for a lift truck connected to a valve assembly 10 according to a preferred embodiment of the present invention.
  • the valve assembly 10 is connected to a control panel 11 by a first hydraulic supply line 12 and a second hydraulic supply line 14.
  • the control panel 11 is connected to a hydraulic fluid tank 16 by a tank supply line 18 and a tank return line 20.
  • a pump (not shown) is connected to the tank supply line 18 to provide the hydraulic fluid under pressure.
  • control panel 11 includes a hydraulic circuit 26 to interchangeably connect the tank supply and return lines 18, 20 to the first and second hydraulic supply lines 12 and 14.
  • the circuit 26 is operated in a conventional manner and will not be further described.
  • the circuit 26 is hydraulically connected to three corresponding levers in the lift truck cab. Other similar circuits may be used to control other vehicle functions such as mast tilting, carriage raising, and the like. For convenience, only the lever 28 for operating the particular circuit 26 is shown. It will be understood by those skilled in the art that other types of actuators may be provided.
  • the valve assembly includes a valve block 30, which preferably has a box-like shape.
  • a first supply port 32 and a second supply port 34 are provided in the valve block 30.
  • the first and second supply ports 32, 34 communicate with first and second hydraulic supply lines 12, 14 (shown in Figure 1 ), respectively.
  • the supply ports 32, 34 are located on the same face of the block 30.
  • An orifice valve 35 (shown in Figures 5A-5D ) is preferably provided between the supply ports 32 and 34. The function of this orifice valve is discussed below.
  • the diameter of the orifice valve may be about 1.09mm (0.043 inches).
  • a first chamber 36 and a second chamber 38 are provided in the valve block 30.
  • the first and second chambers 36, 38 communicate with first and second supply ports 32, 34 via first and second block channels 40 and 42.
  • a first operator port 44 and a second operator port 46 are provided on one face of the block 30, and a third operator port 48 and a fourth operator port 50 are provided on the opposite face of the block 30.
  • the first and second operator ports 44, 46 communicate with the first chamber 36.
  • the third and fourth operator ports 48, 50 communicate with the second chamber 38.
  • the first and third operator ports 44, 48 are connected to corresponding ports (not shown) of a first conventional hydraulic operator 80.
  • the first hydraulic operator may be, for example, a fork positioning cylinder.
  • the second and fourth operator ports 46, 50 are connected to corresponding ports (not shown) of a second hydraulic operator 82.
  • the second hydraulic operator may be, for example, a side shifting cylinder.
  • a pilot channel 52 is provided in the valve block 30.
  • the pilot channel 52 communicates with first and second chambers 36, 38.
  • the pilot channel 52 also communicates with first and second block channels 40, 42, all three meeting at an intersection 54.
  • a bi-directional valve 56 is located in the intersection 54.
  • the bi-directional valve is a conventional ball and shuttle valve. The bi-directional valve alternatively connects pilot channel 52 with block channel 40 or block channel 42.
  • a first conventional selection valve 60 is located in the first chamber 36 and a second conventional selection valve 61 is located in the second chamber 38.
  • the selection valves 60, 61 are identical.
  • such valves are commercially available from various valve manufacturers.
  • One useful example is a valve sold by Hydraforce Inc. (Model No. PD 10-40).
  • the first selection valve 60 includes a generally cylindrical valve housing 62 mounted in the first chamber 36.
  • the cylindrical valve housing 62 has an open end proximate to the pilot channel 52, and defines an internal valve chamber 64.
  • the cylindrical valve housing 62 also includes a plurality of radially directed circumferentially arranged openings 65 for communicating with the first chamber 36.
  • a moving valve body 66 is located within the valve chamber 64 of valve housing 62.
  • the valve body 66 has a pressure surface 68 adjacent the open end of the valve housing 62.
  • the valve body 66 has a narrower portion which defines an annular space 69.
  • the radially directed openings 65 communicate with the annular space 69 between the valve body 66 and the valve housing 62.
  • the valve body 66 is connected to a spring 74 located in a closed end of the cylindrical valve housing 62.
  • Valve body 66 may be moved relative to valve housing 62 by collapsing the spring 74.
  • the spring 74 biases the valve body 66 to the position shown in Figures 5A and 5B .
  • the spring resistance is configured such that a pressure of 2.17 MPa (315 PSI) or greater applied to pressure surface 68 is required to collapse the spring 74 so that the valve body 66 may move to the position shown in Figures 5C and 5D .
  • a number of external O-rings 70, 72 are provided to seal portions of the first selection valve 60 against portions of the wall of the first chamber 36.
  • Internal O-rings (not shown) are also provided to seal the upper and lower ends of the annular space 69 from the remainder of the valve chamber 64 to prevent bleeding of fluid between the valve body 66 and valve housing 62.
  • the second selection valve 61 is the same as the first selection valve 60, it will not be described in detail.
  • valve assembly 10 For convenience, the operation of the present invention will be described in conjunction with a conventional hydraulically-operated fork positioner 80 and side shifter 82 for a lift truck.
  • the first hydraulic operator will be the fork positioner
  • the second hydraulic operator will be the side shifter.
  • the present invention may be operated with any two hydraulic operators requiring different pressure, and is not confined to fork positioners and side shifters, or to hydraulic operators for lift trucks. The operators could be used for any desired function, such as rotating, tilting, clamping, or the like.
  • the lift truck operator when the lift truck operator wishes to actuate the fork positioner in a first direction, such as to narrow the forks, the operator moves the lever 28 part-way in one direction.
  • the circuit 26 is partially activated to supply hydraulic fluid from the hydraulic fluid tank 16 along tank supply line 18, through section 22, and then to the first hydraulic supply line 12. Because, the circuit 26 is only, parity activated, the flow rate of hydraulic fluid in the first hydraulic supply line 12 is low, resulting in low pressure as explained below.
  • low pressure means pressure below 2.17 MPa (315 PSI).
  • the hydraulic fluid enters the first supply port 32 and flows into first channel 40.
  • the pressure of the fluid in first block channel 40 moves the bi-directional valve 56 into a position permitting fluid communication between first block channel 40 and pilot channel 52, while sealing off communication between second block channel 42 and the pilot channel 52.
  • the pressure of the fluid in the pilot channel 52 acts on the pressure surface 68 of each of the selection valves 60, 61. Because the pressure is below 2.17 MPa (315 PSI), neither of the valve bodies 66 of the selection valves 60, 61 move. Accordingly, the annular channels of selection valves 60 and 61 remain aligned with first operator port 44 and third operator port 48, respectively.
  • the supply fluid in first block channel 40 also enters the annular space 69 through the radially directed openings 65 in the cylindrical housing 62 of the first selection valve 60.
  • the fluid exits from the annular space 69 of first selection valve 60 through additional radially directed openings 65 and enters first operator port 44.
  • the fluid is prevented from entering second operator port 46 by O-ring 70 and the internal O-rings of the selection valve 60.
  • the hydraulic fluid travels to the fork positioner 80 by line 84 connected to first operator port 44.
  • hydraulic fluid also leaves the fork positioner 80 and enters third operator port 48 via line 86.
  • the fluid is routed to second block channel 42 through the second selection valve 61, in a similar but reverse manner as described for first selection valve 60.
  • the fluid exits the valve assembly 10 at second supply port 34 along second supply line 14.
  • the operator moves the lever 28 part-way in the opposite direction causing the circuit 26 to partially activate so that section 24 is employed to direct a low pressure flow of fluid from the hydraulic fluid supply tank 16 into the second hydraulic supply line 14.
  • the hydraulic fluid enters the valve block 30 via the second supply port 34 and into the second block channel 42.
  • the bi-directional valve 56 is moved in the other direction such that it is now the second block channel 42 which communicates with the pilot channel 52. Because it is low pressure fluid, neither of the valve bodies 66 of selection valves 60 and 61 move from the position shown in Figure 2B . However, the hydraulic fluid flows through second selection valve 61 in the same manner as described for the first selection valve 60.
  • the hydraulic fluid flows out of third operator port 48 and into line 86 to the fork positioner 80. This causes the fork positioner to operate in the opposite direction.
  • Hydraulic fluid flowing out of fork positioner 80 into line 84 enters the valve assembly 10 at first operator port 44.
  • the returning fluid is directed into first channel 40 by the first selection valve 60, as described above.
  • the fluid exits at first supply port 32 and is returned to the tank return line 20 via first supply line 12.
  • moving the lever 28 either way causes the fork positioner 80 to move in either direction (i.e. narrowing or widening the fork spacing).
  • high pressure means pressure of 2.17 MPa (315 PSI) or higher.
  • the hydraulic fluid enters the first chamber 36 along the same path as described for the narrowing function of the fork positioner.
  • the now high pressure fluid passes to the pilot channel 52 and acts against surface 68 of each of the valve bodies 66 of the selection valves 60 and 61. Because the pressure in the pilot channel 52 acting against pressure surface 68 of each valve body 66 is greater than the resistance of the respective springs 74, the valve body 66 of each selection valve moves against the spring 74. This moves the valve bodies 66 to the positions shown in Figures 5C and 5D , and thereby permits fluid in first block channel 40 to flow through annular space 69 and into second operator port 46. O-ring 72 prevents fluid communication with first operator port 44.
  • hydraulic fluid flows to the side shifter 82 along line 88.
  • Hydraulic fluid returns to fourth operator port 50 along line 90, then through selection valve 61.
  • the fluid flows through the valve block 30 and out through the second supply port 34 in a manner analogous to the manner described above.
  • the fluid is returned to the tank in the same manner as described for the narrowing function of the fork positioner.
  • the hydraulic operators are able to achieve their required functions while operating at different pressures.
  • One pressure is referred to herein as the lower pressure, while the other pressure is referred to as the higher pressure.
  • Absolute values are, of course, widely variable. However, it is preferred that the two pressures differ by about 0.345 MPa (50 PSI).
  • fork positioning can be successfully preformed using pressures of less than 1.72 MPa (250 PSI), while side shifting can be accomplished using pressures above 2.24 MPa (325 PSI).
  • Other pressures and other pressure differentials can be used depending on the vehicle and the implements being controlled.
  • the high pressure in the supply lines 12 and 14 is achieved by moving lever 28 quickly to the full open position in the desired direction.
  • the lever When fork positioning is desired, the lever is moved in the desired direction only part way.
  • the initial fluid pressure available at control panel 11 is usually relatively low and, in any event, only a restricted flow occurs.
  • the restricted flow occurs at a lower pressure, and thus, fluid reaching the valve assembly 10 is at the lower pressure.
  • the forks can be moved using the lower pressure.
  • the restricted fluid continues to flow as the forks move and pressure does not build up in supply lines 12 or 14 or in valve block 30.
  • This means the selection valves 60 and 61, remain in the starting position shown in Figures 2A and 2B under the pressure exerted by spring 74 and fork positioning continues to occur for as long as desired and in the direction desired
  • the orifice valve 35 may be provided to reduce any hammer effect which may be caused by sudden changes in direction of the fluid flow.
  • the preferred embodiment of the invention described above is configured to provide selectable, two-way, hydraulically actuated movement.
  • certain hydraulic operators may require only one way movement.
  • the return movement of the hydraulic operator may be provided by some other source, such as a spring or gravity.
  • the second supply port 34, second block channel 42, second selection valve 61, bi-directional valve 56, and third and fourth operator ports 48, 50 may be omitted.

Claims (18)

  1. Hydraulikventilaggregat (10) zur wahlweisen Abgabe von Hydraulikfluid aus einem Vorrat (16) an Hydraulikfluid an einen aus einem ersten Hydraulikantrieb (80) und einem zweiten Hydraulikantrieb (82), wobei das Aggregat Folgendes umfasst:
    a) ein Ventilblockelement (30), das Folgendes definiert:
    i) eine erste Zufuhröffnung (32), die für Fluidkommunikation mit dem Vorrat (16) angeordnet ist;
    ii) eine zweite Zufuhröffnung (34), die für Fluidkommunikation mit dem Vorrat (16) angeordnet ist;
    iii) eine erste Antriebsöffnung (44), die für Fluidkommunikation mit dem ersten Hydraulikantrieb (80) angeordnet ist;
    iv) eine zweite Antriebsöffnung (46), die für Fluidkommunikation mit dem zweiten Hydraulikantrieb (80) angeordnet ist;
    v) eine dritte Antriebsöffnung (48), die für Fluidkommunikation mit dem ersten Hydraulikantrieb (80) angeordnet ist;
    vi) eine vierte Antriebsöffnung (50), die für Fluidkommunikation mit dem zweiten Hydraulikantrieb (82) angeordnet ist;
    vii) eine erste Kammer (36), wobei die erste Kammer (32) in Fluidkommunikation mit der ersten Zufuhröffnung (32), der ersten Antriebsöffnung (44) und der zweiten Antriebsöffnung (46) ist;
    viii) eine zweite Kammer (38), wobei die zweite Kammer in Fluidkommunikation mit der zweiten Zufuhröffnung (34), der dritten Antriebsöffnung (48) und der vierten Antriebsöffnung (50) ist;
    b) ein erstes Auswahlventil (60), das sich in der ersten Kammer (36) befindet, und ein zweites Auswahlventil (61), das sich in der zweiten Kammer (38) befindet, wobei das erste und das zweite Auswahlventil (60, 61) angeordnet sind, um sich gemeinsam zu bewegen, wobei das erste und das zweite Auswahlventil (60, 61) zwischen einer ersten Position, wenn sich das Hydraulikfluid in einem ersten Druckzustand befindet, und einer zweiten Position, wenn sich das Hydraulikfluid in einem zweiten Druckzustand befindet, betreibbar sind, wobei in der ersten Position das erste Auswahlventil (60) eine Fluidkommunikation zwischen der ersten Zufuhröffnung (32) und der ersten Antriebsöffnung (44) ermöglicht, und das zweite Auswahlventil (61) eine Fluidkommunikation zwischen der zweiten Zufuhröffnung (34) und der dritten Antriebsöffnung (48) ermöglicht, wobei in der zweiten Position das erste Auswahlventil (60) eine Fluidkommunikation zwischen der ersten Zufuhröffnung (32) und der zweiten Antriebsöffnung (46) ermöglicht und das zweite Auswahlventil (61) eine Fluidkommunikation zwischen der zweiten Zufuhröffnung (34) und der vierten Antriebsöffnung (50) ermöglicht;
    worin der erste Druck niedriger als der zweite Druck ist.
  2. Aggregat (10) nach Anspruch 1, ferner umfassend einen Aktuator (28), der wirksam mit dem Vorrat (16) verbunden ist, wobei der Aktuator (28) zwischen einer ersten Aktuatorposition, die ausgebildet ist, um das Hydraulikfluid an die erste Zufuhröffnung (32) in dem ersten Druckzustand abzugeben, einer zweiten Aktuatorposition, die ausgebildet ist, um das Hydraulikfluid an die erste Zufuhröffnung (32) in dem zweiten Druckzustand abzugeben, einer dritten Aktuatorposition, die ausgebildet ist, um das Hydraulikfluid an die zweite Zufuhröffnung (34) in dem ersten Druckzustand abzugeben, und einer vierten Aktuatorposition, die ausgebildet ist, um das Hydraulikfluid an die zweite Zufuhröffnung (34) in dem zweiten Druckzustand abzugeben, wahlweise bewegbar ist, wobei die erste und die dritte Aktuatorposition ausgebildet sind, um eine Hin- und Her-Bewegung des ersten Hydraulikantriebs (80) zu ermöglichen, und die zweite und vierte Aktuatorposition die Hin- und Her-Bewegung des zweiten Hydraulikantriebs (82) ermöglichen.
  3. Aggregat (10) nach Anspruch 2, worin, wenn sich der Aktuator (28) in der ersten oder zweiten Position befindet, das Hydraulikfluid aus der zweiten Zufuhröffnung (34) zum Vorrat zurückgeführt wird, und wenn sich der Aktuator (28) in der dritten oder vierten Position befindet, das Hydraulikfluid aus der ersten Zufuhröffnung (32) zum Vorrat (16) zurückgeführt wird.
  4. Aggregat (10) nach Anspruch 3, worin der Aktuator (28) einen mit dem Hydraulikkreis (26) verbundenen Hebel umfasst.
  5. Aggregat (10) nach Anspruch 4, worin der Hebel (28) aus einer zentralen Ruhestellung in zwei entgegengesetzte Richtungen bewegbar ist, worin sich der Hebel (28) in der ersten Aktuatorposition teilweise in eine Richtung bewegt und sich der Hebel (28) in der dritten Aktuatorposition teilweise in eine entgegengesetzte Richtung bewegt, wobei sich der Hebel (28) in der zweiten Aktuatorposition im Wesentlichen vollständig in die eine Richtung bewegt und sich der Hebel (28) in der vierten Aktuatorposition im Wesentlichen vollständig in die entgegengesetzte Richtung bewegt.
  6. Aggregat (10) nach Anspruch 1, worin das Ventilblockelement (30) einen Pilotkanal (52) definiert, wobei der Pilotkanal (52) angeordnet ist, um in Fluidkommunikation mit der ersten Kammer (36), der zweiten Kammer (38) und einer aus der ersten Zufuhröffnung (32) und der zweiten Zufuhröffnung (34) zu sein, wobei das erste und das zweite Auswahlventil (60, 61) angeordnet sind, um mittels Druck in den Pilotkanal (52) bewegt zu werden.
  7. Aggregat (10) nach Anspruch 6, worin das Ventilblockelement (30) einen ersten und einen zweiten Blockkanal (40, 42) definiert, wobei sich der erste Blockkanal (40) zwischen der ersten Zufuhröffnung (32) und der ersten Kammer (36) erstreckt, wobei sich der zweite Blockkanal (42) zwischen der zweiten Zufuhröffnung (34) und der zweiten Kammer (38) erstreckt.
  8. Aggregat (10) nach Anspruch 7, ferner umfassend ein bidirektionales Ventil (54), das an der Übergangsstelle zwischen dem Pilotkanal (52), dem ersten Blockkanal (40) und dem zweiten Blockkanal (42) angeordnet ist, wobei das bidirektionale Ventil (54) angeordnet ist, um Fluidkommunikation zwischen dem ersten Blockkanal (40) und dem Pilotkanal (52), wenn das Hydraulikfluid in die erste Zufuhröffnung (32) strömt, und zwischen dem zweiten Blockkanal (42) und dem Pilotkanal (52) bereitzustellen, wenn das Hydraulikfluid in die zweite Zufuhröffnung (34) strömt.
  9. Aggregat (10) nach Anspruch 8, worin das bidirektionale Ventil (54) ein Kugel- und Wechselventil umfasst.
  10. Aggregat (10) nach Anspruch 8, worin das erste Auswahlventil (60) Folgendes umfasst:
    a) ein Ventilgehäuse (62), das ein offenes Ende nahe dem Pilotkanal (52) und ein entgegengesetztes geschlossenes Ende definiert, wobei das Ventilgehäuse eine innere Ventilkammer (64) definiert, die mit dem offenen Ende kommuniziert;
    b) einen Ventilkörper (66), der bewegbar in der inneren Ventilkammer (64) aufgenommen ist, wobei der Ventilkörper (66) eine Druckoberfläche (68) nahe dem offenen Ende der inneren Ventilkammer (64) definiert, worin der Ventilkörper (66) mittels Druck in dem Pilotkanal (52), der auf die Druckoberfläche (68) ausgeübt wird, aus der ersten Position in die zweite Position bewegt wird; und
    c) ein Vorspannmittel (74), um den Ventilkörper (66) zur ersten Position hin zu drücken.
  11. Aggregat (10) nach Anspruch 10, worin das Vorspannmittel (74) in dem geschlossenen Ende des Ventilgehäuses (62) angeordnet ist.
  12. Aggregat (10) nach Anspruch 11, worin das Vorspannmittel (74) eine Feder umfasst.
  13. Aggregat (10) nach Anspruch 12, worin ein gegen die Druckoberfläche (68) wirkender Druck von 2,17 MPa (315 PSI) oder mehr erforderlich ist, um den Widerstand der Feder (76) zu überwinden.
  14. Aggregat (10) nach Anspruch 13, worin das Ventilgehäuse (62) eine Vielzahl entlang des Umfangs angeordnete Öffnungen (65) definiert.
  15. Aggregat (10) nach Anspruch 14, worin das zweite Auswahlventil (61) im Wesentlichen mit dem ersten Auswahlventil (60) ident ist.
  16. Aggregat (10) nach Anspruch 8, worin der erste Hydraulikantrieb (80) ein Gabelpositionsaggregat für einen Hubstapler, und der zweite Hydraulikantrieb (82) ein Seitenverschieberaggregat für einen Hubstapler ist.
  17. Aggregat (10) nach Anspruch 12, worin das Ventilblockelement (30) kastenförmig ist, wobei das Ventilblockelement eine erste Fläche, eine zweite Fläche und eine dritte Fläche definiert.
  18. Aggregat (10) nach Anspruch 17, worin die erste und die zweite Zufuhröffnung (32, 34) auf der ersten Fläche angeordnet sind, wobei die erste und die zweite Antriebsöffnung (44, 46) auf der zweiten Fläche angeordnet sind und die dritte und vierte Antriebsöffnung (48, 50) auf der dritten Fläche angeordnet sind.
EP20030701411 2002-03-01 2003-02-14 Hydraulisches ventilaggregat für mehrere funktionen Expired - Lifetime EP1481168B1 (de)

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
US36107502P 2002-03-01 2002-03-01
US361075P 2002-03-01
US120789 2002-04-12
US10/120,789 US6782910B2 (en) 2002-03-01 2002-04-12 Multi-function hydraulic valve assembly
PCT/CA2003/000212 WO2003074884A1 (en) 2002-03-01 2003-02-14 Multi-function hydraulic valve assembly

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EP1481168A1 EP1481168A1 (de) 2004-12-01
EP1481168B1 true EP1481168B1 (de) 2009-09-30

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JP (1) JP2005519244A (de)
CN (1) CN100404882C (de)
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AU (1) AU2003203106A1 (de)
CA (1) CA2476759C (de)
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Cited By (1)

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Publication number Priority date Publication date Assignee Title
DE102014101764A1 (de) * 2014-02-12 2015-08-13 Jungheinrich Aktiengesellschaft Steuerblock für ein Hydrauliksystem eines Flurförderzeugs mit mindestens einem Hydraulikventil

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104803290B (zh) * 2015-04-21 2017-04-12 青岛港国际股份有限公司 一种岸桥提升机构和采用其提升岸桥构件的方法

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NL7203122A (de) * 1972-03-09 1973-09-11
US3782249A (en) * 1972-11-16 1974-01-01 Allis Chalmers Hydraulic control system with locking valve to prevent accidental or unauthorized lowering of a tractor implement
CN1017276B (zh) * 1988-02-17 1992-07-01 通用电气公司 液体多通道转换器
CN1021648C (zh) * 1989-10-04 1993-07-21 日本石油化学株式会社 升降叉车
US5139385A (en) * 1990-04-03 1992-08-18 Swingshift Manufacturing, Inc. Dual pallet fork attachment for a lift truck
FR2720123B1 (fr) * 1994-05-19 1996-08-14 France Power Packer Sa Automatisme de commande hydraulique, notamment pour charrue.

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102014101764A1 (de) * 2014-02-12 2015-08-13 Jungheinrich Aktiengesellschaft Steuerblock für ein Hydrauliksystem eines Flurförderzeugs mit mindestens einem Hydraulikventil

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CN100404882C (zh) 2008-07-23
DE60329471D1 (de) 2009-11-12
CN1639467A (zh) 2005-07-13
EP1481168A1 (de) 2004-12-01
JP2005519244A (ja) 2005-06-30
CA2476759C (en) 2011-07-26
ATE444449T1 (de) 2009-10-15
AU2003203106A1 (en) 2003-09-16
CA2476759A1 (en) 2003-09-12

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