EP0743459B1 - Elektrohydraulisches Hubmodul - Google Patents
Elektrohydraulisches Hubmodul Download PDFInfo
- Publication number
- EP0743459B1 EP0743459B1 EP96106917A EP96106917A EP0743459B1 EP 0743459 B1 EP0743459 B1 EP 0743459B1 EP 96106917 A EP96106917 A EP 96106917A EP 96106917 A EP96106917 A EP 96106917A EP 0743459 B1 EP0743459 B1 EP 0743459B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- control
- lifting module
- module according
- restrictor
- line
- 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
Links
Images
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
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
- F15B11/04—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
- F15B11/05—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed specially adapted to maintain constant speed, e.g. pressure-compensated, load-responsive
-
- 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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/40—Flow control
- F15B2211/405—Flow control characterised by the type of flow control means or valve
- F15B2211/40515—Flow control characterised by the type of flow control means or valve with variable throttles or orifices
-
- 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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/40—Flow control
- F15B2211/415—Flow control characterised by the connections of the flow control means in the circuit
- F15B2211/41563—Flow control characterised by the connections of the flow control means in the circuit being connected to a pressure source and a return line
-
- 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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/40—Flow control
- F15B2211/42—Flow control characterised by the type of actuation
- F15B2211/428—Flow control characterised by the type of actuation actuated by fluid pressure
-
- 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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/40—Flow control
- F15B2211/45—Control of bleed-off flow, e.g. control of bypass flow to the return line
-
- 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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/50—Pressure control
- F15B2211/505—Pressure control characterised by the type of pressure control means
- F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
- F15B2211/50536—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using unloading valves controlling the supply pressure by diverting fluid to the return line
-
- 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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/50—Pressure control
- F15B2211/515—Pressure control characterised by the connections of the pressure control means in the circuit
- F15B2211/5157—Pressure control characterised by the connections of the pressure control means in the circuit being connected to a pressure source and a return line
-
- 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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/50—Pressure control
- F15B2211/52—Pressure control characterised by the type of actuation
- F15B2211/528—Pressure control characterised by the type of actuation actuated by fluid pressure
-
- 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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/60—Circuit components or control therefor
- F15B2211/635—Circuits providing pilot pressure to pilot pressure-controlled fluid circuit elements
- F15B2211/6355—Circuits providing pilot pressure to pilot pressure-controlled fluid circuit elements having valve means
-
- 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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
- F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
- F15B2211/7051—Linear output members
- F15B2211/7052—Single-acting output 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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/80—Other types of control related to particular problems or conditions
- F15B2211/85—Control during special operating conditions
- F15B2211/851—Control during special operating conditions during starting
-
- 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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/80—Other types of control related to particular problems or conditions
- F15B2211/86—Control during or prevention of abnormal conditions
- F15B2211/8613—Control during or prevention of abnormal conditions the abnormal condition being oscillations
Definitions
- the invention relates to an electro-hydraulic lifting module specified in the preamble of claim 1.
- a forklift-tight pressure compensator is a special feature because it is able to hold the load or the load pressure in a forklift truck without further aids.
- the regulating piston of the pressure compensator can be moved with a tight fit in the housing bore and is held in the closed end position with a positive overlap in order to seal separate orifices in the drain line against one another.
- Forklift tightness means that a leakage between 7 and 10 cm 3 / min is tolerable.
- This pressure compensator works with a leakage> 1.0cm 3 / min.
- a damping throttle is provided to prevent pressure fluctuations in the control system of the lifting module. Because pressure fluctuations are transferred to the hydraulic motor and are extremely undesirable.
- EP-A-0 279 315 and EP-A-0 056 423 For the technological background, reference should be made to EP-A-0 279 315 and EP-A-0 056 423.
- the invention has for its object an electrohydraulic Lift module of the type mentioned at the beginning improve that while maintaining the evaporation of pressure fluctuations optimized response behavior in the control system is reached when the pressure compensator is opened.
- the bypass channel bypasses the damping throttle as long as the control piston from the closed end position almost to one initial opening position moved. Just before, just after or exactly during the control piston the connection in the drain line opens, the bypass channel is closed, so that Control pressure medium takes the path via the damping throttle Dampens pressure fluctuations.
- the bypass channel is then excluded Function and remains even during the game movements of the control piston to comply with the set on the orifice plate Pressure difference without influencing the movement of the control pressure medium in the control line. It results while maintaining the advantageous damping effect an optimal response the stack-tight pressure compensator.
- the position of the Mouth of the bypass canal to the extent of the positive coverage of the control piston It will be the time predetermined at which to start from the control chamber dampened control pressure medium to dampen pressure fluctuations to suppress.
- the bypass channel shut off reliably during the game movements of the control piston.
- the Beipbelkanal a throttling, which is, however, less than that Throttling of the damping throttle.
- the embodiment according to claim is particularly expedient 5, because a cascade throttle even with small amounts of control pressure medium, as it usually moves in a control circuit high damping is generated.
- cascade reactors inexpensive and available in many settings.
- the damping throttle is a threaded throttle, the bypass channel in the initial movement of the control piston.
- the embodiment according to claim 9 is structurally simple the screw-in valve insert is screwed into the mounting hole becomes.
- an external thread section the cartridge valve insert to form the Threaded throttle used so that it has a double function Fulfills.
- the cascade throttle integrated in the valve element of the check valve, which saves installation space and reduces the number of individual parts.
- the flow path leading over the cascade throttle is from Bypass channel bypassed as long as the control piston is in the direction moved to the initial open position.
- the embodiment according to claim 12 is advantageous because the cap closes the flow path and the insert to the outside covers.
- Fig. 1 illustrates a hydraulic control device, for example for a forklift, which is largely in DE-A1-42 39 321 described control devices is similar that to minor details for the invention or detailed functions referenced to this prior publication becomes.
- a hydro consumer e.g. the lifting cylinder a forklift, is controlled from a work line H, via a switching valve 1 from a pump line P can be supplied with pressure medium.
- the switching valve 1 is actuated by means of a magnet 2.
- From the work management H branches off a drain line 3, which via a branch 3 'to one Return line R is connected and an electro-hydraulic Contains lifting module M with which at least the lowering movements of the lifting cylinder are electrically controllable.
- the lifting module M contains an orifice B and downstream of orifice B one Pressure compensator W.
- the position of the orifice plate B is via a pilot valve V set using a proportional magnet 9 as a function of its current supply from the illustrated Position against a spring is adjustable.
- the positions of the orifice plate B and the pressure compensator W can be in the drain line 3 are also interchanged. It is also possible the orifice plate B directly through the proportional magnet 9 to operate. In any case, it must be ensured that the the closing and opening sides of the pressure compensator Control lines of the pressure compensator give up the pressure difference, which is set via the orifice B.
- control line 3 branches from a control line 4 leading to the closing side of a control piston 10 containing pressure compensator W. From the control line 4 branches a control line 5 to a connection of the Pilot valve V from. Between the orifice plate B and the Pressure compensator W branches off from drain line 3 at point 6 Control line 7 from the one hand to the closing side of the metering orifice B and to the opening side of the pressure compensator W and on the other to a second connection of the pilot valve V and to the pilot solenoid 9 facing the pilot solenoid leads. An opposite connection of the pilot valve V is via a further control line 8 with the opening side the orifice B connected, in the control line 8 a damping throttle D1 can be provided.
- a damping throttle D2 is provided, which in Closing direction of the pressure compensator W by means of a parallel check valve R is avoidable. Furthermore (indicated by dotted lines) a bypassing the damper D2 and the check valve Beyp motherboardkanal Y provided on the in detail at the Explanation of Fig. 2 will be discussed.
- the pressure compensator is opened in the opening direction by a control spring 11 acted upon.
- the damping throttle D2 dampens pressure fluctuations and the opening movement of the control piston 10 or the pressure compensator W with blocking check valve R.
- the check valve R opens as soon as the pressure compensator is closed, so that then the damper D2 is bypassed.
- the control piston 10 of the pressure compensator W is in one Housing bore 22 of a housing 12 slidably guided also contains the orifice plate B.
- the control piston 10 is with a small fit of just a few microns in the housing bore 22 fitted and works with positive overlap to in the closed end position shown in the upper half of the figure the mouth of the drain line 3 reliably opposite to seal the mouth of the branch 3 'of the drain line.
- the positive coverage can be between 2 and 10 mm, preferably be between 2 and 2.5 mm.
- the control piston 10 has one Circumferential groove 25 with a flank 26, which with aperture the mouths of the drain line 3 and the branch 3 'of the drain line works together.
- Adjacent to edge 26 is one Sealing zone provided on the control piston 10 that with the wall the housing bore 22 cooperates.
- the control spring 11 acts the control piston 10 on the same side as the pressure in the control line 7, namely opposite to the pressure in a control chamber 23 at the right-hand end of the housing bore 22.
- the control line 4 or its branch 4 ' opens into the Chamber 23.
- a bypass line Y is provided, the Mouth 28 arranged in the wall of the housing bore 37 in this way is that they have a trailing edge 27 of the control piston 10 and with a sealing surface adjacent to the barrier edge 27 37 works together.
- the bypass channel Y bypasses one Receiving hole 13 in the housing 12 and leads from the control chamber 23 directly to the control line 4.
- a screw-in valve insert E with a screw-in housing 14 screwed in, which contains a valve seat 15.
- a capsule-shaped valve element 17 included that with the valve seat 15 as a check valve R works together and by a valve spring 29 in the closing direction is applied.
- the valve element 17 is hollow formed and contains a longitudinal flow path, which opens into the valve seat 15.
- the damping throttle D2 here in the form of a cascade throttle 18, contain.
- the screw-in housing 14 has another Longitudinal passage 16 and a transverse channel 20.
- a cap 21 is screwed on opposite seals the housing 12 and the flow path to or from branch 4 'of the control channel closes.
- a turning aid 19 is molded.
- the cap 21 has one Hexagon head.
- the mouth 28 of the bypass channel Y is arranged so that it in the closing end position shown in FIG. 2, upper half of the control piston 10 is free and the control chamber 23 under Bypassing the check valve R and the damping throttle D2 directly connects to the control line 4.
- Muzzle 28 is initially free until the flank 26 is aligned with the mouth of branch 3 'of the control line overlaps and one Establishes connection.
- the mouth 28 is closed and the Passivation channel passivated.
- the bypass channel Y With a further movement of the control piston 10 towards the full open position (lower half of Fig. 2) the bypass channel Y remains closed; the control pressure medium must travel through the damping throttle Take D2.
- the orifice plate B has an orifice piston 31 which is in a Housing bore 30 is axially adjustable, namely after Providing the pressures in the control lines 7 and 8 and one Spring 32.
- An adjusting screw 33 is used to adjust the Limit quantity of orifice B.
- the damping throttle is D2 a so-called thread choke, formed by interlocking Thread 35 on the screw-in housing 34 of the screw-in valve insert E and the thread 36 of the receiving bore.
- the valve seat 15 is provided with which, for example, a valve element designed as a ball 18 works together by a spring 29 in the closing direction is charged.
- the further structure of the cartridge valve insert E corresponds to that of Fig. 2.
- the bypass channel Y bypasses the check valve and the damping throttle D2.
- a thread choke or the cascade choke shown could also be another choke, e.g. with an adjustable Throttle element can be used.
- the cascade choke 18 of FIG. 2 consists of a large number of cascade elements designed as aperture plates and combined into a package, the individual Aperture plates separated by spacer rings are spaced. Each aperture plate contains one small through hole.
- the first aperture plates in the package can have several small through holes to to serve as a filter for contaminants.
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- Engineering & Computer Science (AREA)
- Transportation (AREA)
- Structural Engineering (AREA)
- Mechanical Engineering (AREA)
- Civil Engineering (AREA)
- Geology (AREA)
- Combustion & Propulsion (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Life Sciences & Earth Sciences (AREA)
- Chemical & Material Sciences (AREA)
- Forklifts And Lifting Vehicles (AREA)
- Apparatuses And Processes For Manufacturing Resistors (AREA)
- Discharge Heating (AREA)
- Control Of Fluid Pressure (AREA)
- Fluid-Pressure Circuits (AREA)
- Encapsulation Of And Coatings For Semiconductor Or Solid State Devices (AREA)
Description
- Fig. 1
- ein Blockschaltbild einer hydraulischen Steuervorrichtung mit einem elektrohydraulischen Modul,
- Fig. 2
- einen Teilschnitt einer gegenständlichen Ausführungsform des Hubmoduls von Fig. 1, und
- Fig. 3
- eine Detailvariante in einem Schnitt.
Claims (12)
- Elektrohydraulisches Hubmodul (M) für einen einseitig aus einer Druckquelle (P) über eine Arbeitsleitung (H) beaufschlagbaren Hydroverbraucher, insbesondere einen Hubzylinder, mit einem Zweiwege-Mengenregler (B, W) in einer zwischen der Arbeitsleitung (H) und einer Rücklaufleitung (R) angeordneten Ablaßleitung (3'), wobei der Zweiwege-Mengenregler eine mittels eines Proportionalmagneten verstellbare Meßblende (B) und eine staplerdicht ausgebildete Druckwaage (W) mit einem Regelkolben (10) aufweist, der schließseitig aus einer ersten Steuerleitung (4) gegen eine Regelfeder (11) und öffnungsseitig durch die Regelfeder (11) und aus einer zweiten Steuerleitung (7) beaufschlagt ist, und mit einer Dämpfdrossel (D2) für zumindest den Öffnungshub des Regelkolbens (10) der Druckwaage (W), dadurch gekennzeichnet, daß die schließseitige Steuerkammer (23) der Druckwaage (W) über einen Beipaßkanal (Y) an die erste Steuerleitung (4) angeschlossen ist, daß der Beipaßkanal (Y) die Dämpfdrossel (D2) umgeht, und daß die Mündung (28) des Beipaßkanals (Y) in einer Wand der Steuerkammer (23) derart angeordnet ist, daß sie bei einem Hub des Regelkolbens (10) aus dessen Schließendstellung bis in etwa zu einer anfänglichen Öffnungsstellung der Druckwaage (W) frei und beim weiteren Öffnungshub des Regelkolbens in etwa ab der anfänglichen Öffnungsstellung vom Regelkolben (10) abgesperrt ist.
- Hubmodul nach Anspruch 1, dadurch gekennzeichnet, daß zwischen einer Einlaßmündung und einer Auslaßmündung der Ablaßleitung (3, 3') zum Regelkolben (10) ein axialer Zwischenabstand (positive Überdeckung) vorgesehen ist, und daß in der Schließendstellung des Regelkolbens (10) der in Öffnungshubrichtung gesehene Abstand zwischen einer Absperrkante (27) des Regelkolbens (10) und dem in dieser Hubrichtung hinten liegenden Rand der Mündung (28) des Beipaßkanals (27) annähernd dem Zwischenabstand entspricht.
- Hubmodul nach den Ansprüchen 1 und 2, dadurch gekennzeichnet, daß der Regelkolben (10) angrenzend an die Absperrkante (27) eine Dichtfläche (37) zum Absperren der Mündung (28) des Beipaßkanals (Y) aufweist.
- Hubmodul nach Anspruch 1, dadurch gekennzeichnet, daß der Beipaßkanal (Y) einen kleineren Querschnitt besitzt als die Steuerleitung (4, 4'), z.B. einen Durchmesser von ca. 1 mm gegenüber einem Durchmesser von ca. 4 mm der Steuerleitung.
- Hubmodul nach Anspruch 1, dadurch gekennzeichnet, daß die Dämpfdrossel (D2, D1) eine Kaskadendrossel (18) mit einer Vielzahl von Kaskadenelementen ist.
- Hubmodul nach Anspruch 1, dadurch gekennzeichnet, daß die Dämpfdrossel (D2, D1) eine Gewindedrossel ist, bei der ein gedrosselter Strömungsweg zwischen ineinandergreifenden Gewindegängen von Innen- und Außengewinden (35, 36) gebildet ist.
- Hubmodul nach Anspruch 1, dadurch gekennzeichnet, daß die Dämpfdrossel (D1, D2) ein verstellbares Drosselelement aufweist.
- Hubmodul nach den Ansprüchen 1, 5 und 6, dadurch gekennzeichnet, daß die Dämpfdrossel (D2) in Strömungsrichtung zur Schließseite der Druckwaage (W) über ein Rückschlagventil (R) umgehbar ist, und daß die Dämpfdrossel (D2) in dem Rückschlagventil (R) angeordnet ist.
- Hubmodul nach den Ansprüchen 1, 5, 6 und 8, dadurch gekennzeichnet, daß das Rückschlagventil (R) ein in eine die Steuerleitung (4, 4') schneidende Aufnahmebohrung (13) eines Gehäuses (12) zumindest der Druckwaage (W) eingeschraubter Einschraubventil-Einsatz (E) ist, der ein federbelastetes Ventilelement (17) und einen Ventilsitz (15) aufweist.
- Hubmodul nach den Ansprüchen 1, 6 und 9, dadurch gekennzeichnet, daß der Einschraubventileinsatz (E) einen Außengewindeabschnitt (35) aufweist, der in ein Innengewinde (36) der Aufnahmebohrung (13) eingeschraubt ist und mit diesem die Gewindedrossel bildet.
- Hubmodul nach den Ansprüchen 1, 5 und 9, dadurch gekennzeichnet, daß das Ventilelement (17) des Rückschlagventils (R) als Kapsel mit einem in den Ventilsitz (15) mündenden Strömungsweg ausgebildet ist, und daß die Kaskadendrossel (18) in der Kapsel angeordnet ist.
- Hubmodul nach den Ansprüchen 9 bis 11, dadurch gekennzeichnet, daß auf den aus der Aufnahmebohrung (13) vorstehenden Einschraubventil-Einsatz (E) eine gegen das Gehäuse (12) abdichtende Kappe (21) aufgeschraubt ist.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE29508394U DE29508394U1 (de) | 1995-05-19 | 1995-05-19 | Elektrohydraulisches Hubmodul |
DE29508394U | 1995-05-19 |
Publications (2)
Publication Number | Publication Date |
---|---|
EP0743459A1 EP0743459A1 (de) | 1996-11-20 |
EP0743459B1 true EP0743459B1 (de) | 1998-08-12 |
Family
ID=8008337
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP96106917A Expired - Lifetime EP0743459B1 (de) | 1995-05-19 | 1996-05-02 | Elektrohydraulisches Hubmodul |
Country Status (5)
Country | Link |
---|---|
EP (1) | EP0743459B1 (de) |
AT (1) | ATE169723T1 (de) |
DE (2) | DE29508394U1 (de) |
DK (1) | DK0743459T3 (de) |
ES (1) | ES2122741T3 (de) |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE19716442A1 (de) * | 1997-04-20 | 1998-10-22 | Eckehart Schulze | Hydraulik-Installation an einem Gabelstapler-Fahrzeug |
Family Cites Families (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
ATE14919T1 (de) * | 1981-01-16 | 1985-08-15 | Heilmeier & Weinlein | Elektromagnet-betaetigtes mehrstellungs/mehrwege- hydraulikventil. |
DE3705170C1 (de) * | 1987-02-18 | 1988-08-18 | Heilmeier & Weinlein | Hydraulische Steuervorrichtung |
DE4239321C2 (de) * | 1992-11-23 | 1995-11-09 | Heilmeier & Weinlein | Elektrohydraulisches Hubmodul |
-
1995
- 1995-05-19 DE DE29508394U patent/DE29508394U1/de not_active Expired - Lifetime
-
1996
- 1996-05-02 DK DK96106917T patent/DK0743459T3/da active
- 1996-05-02 AT AT96106917T patent/ATE169723T1/de not_active IP Right Cessation
- 1996-05-02 DE DE59600416T patent/DE59600416D1/de not_active Expired - Lifetime
- 1996-05-02 ES ES96106917T patent/ES2122741T3/es not_active Expired - Lifetime
- 1996-05-02 EP EP96106917A patent/EP0743459B1/de not_active Expired - Lifetime
Also Published As
Publication number | Publication date |
---|---|
ATE169723T1 (de) | 1998-08-15 |
ES2122741T3 (es) | 1998-12-16 |
EP0743459A1 (de) | 1996-11-20 |
DE59600416D1 (de) | 1998-09-17 |
DK0743459T3 (da) | 1999-05-17 |
DE29508394U1 (de) | 1995-08-03 |
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