EP0743459B1 - Electrohydraulic lifting device - Google Patents
Electrohydraulic lifting device 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
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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
- 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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- 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)
- Fluid-Pressure Circuits (AREA)
- Apparatuses And Processes For Manufacturing Resistors (AREA)
- Discharge Heating (AREA)
- Forklifts And Lifting Vehicles (AREA)
- Control Of Fluid Pressure (AREA)
- Encapsulation Of And Coatings For Semiconductor Or Solid State Devices (AREA)
Abstract
Description
Die Erfindung betrifft ein elektrohydraulisches Hubmodul der
im Oberbegriff des Patentanspruchs 1 angegebenen Art.The invention relates to an electro-hydraulic lifting module
specified in the preamble of
Bei einem aus DE-A1-42 39 321 bekannten Hubmodul ist eine staplerdichte Druckwaage ein besonderes Merkmal, weil diese in der Lage ist, bei einem Hubstapler die Last bzw. den Lastdruck ohne weitere Hilfsmittel zu halten. Der Regelkolben der Druckwaage ist mit enger Passung in der Gehäusebohrung verschiebbar und wird mit einer positiven Überdeckung in der Schließendstellung gehalten, um getrennte Mündungen in der Ablaßleitung gegeneinander abzudichten. Staplerdichtigkeit bedeutet, daß eine Leckage zwischen 7 und 10 cm3/min tolerierbar ist. Diese Druckwaage arbeitet mit einer Leckage >1,0cm3/min. Um Druckschwingungen im Steuersystem des Hubmoduls zu vermeiden, ist eine Dämpfdrossel vorgesehen. Denn Druckschwankungen übertragen sich auf den Hydromotor und sind außerordentlich unerwünscht. Allerdings wird zumeist nur die Öffnungsbewegung der Druckwaage gedämpft, weil der Beginn einer Absenkbewegung der Last eine hinsichtlich Druckschwankungen besonders kritische Betriebssituation ist. Die Öffnungsbewegung der Druckwaage aus der Schließendstellung des Regelkolbens hat dann gegen die dämpfende Wirkung der Dämpfdrossel zu erfolgen, was ein unerwünscht verzögertes Ansprechen bewirkt.In a lifting module known from DE-A1-42 39 321, 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. However, usually only the opening movement of the pressure compensator is damped because the start of a lowering movement of the load is an especially critical operating situation with regard to pressure fluctuations. The opening movement of the pressure compensator from the closed end position of the control piston must then take place against the damping effect of the damping throttle, which causes an undesired delayed response.
Zum technologischen Hintergrund ist hinzuweisen auf EP-A-0 279 315 und 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.
Der Erfindung liegt die Aufgabe zugrunde, ein elektrohydraulisches Hubmodul der eingangs genannten Art dahingehend zu verbessern, daß unter Beibehalt der Abdampfung von Druckschwankungen im Steuersystem ein optimiertes Ansprechverhalten beim Öffnen der Druckwaage erreicht wird. 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.
Die gestellte Aufgabe wird mit den im Anspruch 1 enthaltenen
Merkmalen gelöst.The task is with those contained in
Der Beipaßkanal umgeht die Dämpfdrossel, solange sich der Regelkolben aus der Schließendstellung annähernd bis in eine anfängliche Öffnungsstellung bewegt. Kurz bevor, kurz nachdem oder exakt während der Regelkolben die Verbindung in der Ablaßleitung öffnet, wird der Beipaßkanal verschlossen, so daß Steuerdruckmittel den Weg über die Dämpfdrossel nimmt, die Druckschwankungen abdämpft. Der Beipaßkanal ist dann außer Funktion und bleibt auch während der Spielbewegungen des Regelkolbens zum Einhalten der an der Meßblende eingestellten Druckdifferenz ohne Einflußnahme auf die Bewegung des Steuerdruckmittels in der Steuerleitung. Es ergibt sich unter Beibehalt der vorteilhaften Dämpfwirkung ein optimales Ansprechverhalten der staplerdichten Druckwaage.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.
Bei der Ausführungsform gemäß Anspruch 2 ist die Position der Mündung des Beipaßkanals auf das Ausmaß der positiven Überdeckung des Regelkolbens abgestimmt. Es wird der Zeitpunkt vorherbestimmt, an dem begonnen wird, aus der Steuerkammer verdrängtes Steuerdruckmittel zu dämpfen, um Druckschwankungen zu unterdrücken.In the embodiment according to claim 2, 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.
Bei der Ausführungsform gemäß Anspruch 3 wird der Beipaßkanal
während der Spielbewegungen des Regelkolbens zuverlässig abgesperrt.In the embodiment according to
Bei der Ausführungsform gemäß Anspruch 4 erbringt auch der
Beipaßkanal eine Drosselung, die jedoch geringer ist als die
Drosselung der Dämpfdrossel.In the embodiment according to
Besonders zweckmäßig ist die Ausführungsform gemäß Anspruch
5, weil eine Kaskadendrossel auch bei kleinen Steuerdruckmittelmengen,
wie sie üblicherweise in einem Steuerkreis bewegt
werden, eine hohe Dämpfung erzeugt. Ferner sind Kaskadendrosseln
kostengünstig und in den vielen Einstellungen erhältlich.The embodiment according to claim is particularly
Alternativ ist die Dämpfdrossel gemäß Anspruch 6 eine Gewindedrossel, die der Beipaßkanal bei der anfänglichen Bewegung des Regelkolbens umgeht.Alternatively, the damping throttle is a threaded throttle, the bypass channel in the initial movement of the control piston.
Schließlich ist es auch möglich, die Dämpfdrossel gemäß Anspruch 7 mittels eines einstellbaren Drosselelementes auszubilden.Finally, it is also possible to claim the damping throttle 7 by means of an adjustable throttle element.
Um eine Verzögerung der Schließbewegung der Druckwaage zu vermeiden, ist bei der Ausführungsform gemäß Anspruch 8 ein Rückschlagventil vorgesehen, das bei der Öffnungsbewegung sperrt und das Steuerdruckmittel über die Dämpfdrossel zwingt.To delay the closing movement of the pressure compensator avoid is in the embodiment according to claim 8 Check valve provided that the opening movement locks and the control pressure medium via the damping throttle forces.
Baulich einfach ist die Ausführungsform gemäß Anspruch 9, bei
der der Einschraubventileinsatz in die Aufnahmebohrung eingeschraubt
wird.The embodiment according to
Bei der Ausführungsform gemäß Anspruch 10 wird ein Außengewindeabschnitt
des Einschraubventileinsatzes zur Bildung der
Gewindedrossel herangezogen, so daß er eine Doppelfunktion
erfüllt.In the embodiment according to
Bei der Ausführungsform gemäß Anspruch 11 ist die Kaskadendrossel
in das Ventilelement des Rückschlagventils integriert,
was Bauraum spart und die Anzahl der Einzelteile vermindert.
Der über die Kaskadendrossel führende Strömungsweg wird vom
Beipaßkanal umgangen, solange der Regelkolben sich in Richtung
zur anfänglichen Öffnungsstellung bewegt.In the embodiment according to
Die Ausführungsform gemäß Anspruch 12 ist vorteilhaft, weil
die Kappe den Strömungsweg schließt und den Einsatz nach außen
abdeckt. The embodiment according to
Anhand der Zeichnungen werden Ausführungsformen des Erfindungsgegenstandes erläutert. Es zeigen:
- 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.
- Fig. 1
- 2 shows a block diagram of a hydraulic control device with an electrohydraulic module,
- Fig. 2
- a partial section of a concrete embodiment of the lifting module of Fig. 1, and
- Fig. 3
- a detailed variant in one cut.
Fig. 1 verdeutlicht eine hydraulische Steuervorrichtung, beispielsweise für einen Hubstapler, die weitgehend in der DE-A1-42 39 321 beschriebenen Steuervorrichtungen gleicht, so daß zu für die Erfindung nebensächlichen Detailausbildungen oder Detailfunktionen auf diese Vorveröffentlichung verwiesen wird.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.
Ein nicht-dargestellter Hydroverbraucher, z.B. der Hubzylinder
eines Hubstaplers, wird aus einer Arbeitsleitung H angesteuert,
die über ein Schaltventil 1 aus einer Pumpenleitung
P mit Druckmittel versorgbar ist. Das Schaltventil 1 wird
mittels eines Magneten 2 betätigt. Von der Arbeitsleitung H
zweigt eine Ablaßleitung 3 ab, die über einen Ast 3' an eine
Rücklaufleitung R angeschlossen ist und ein elektrohydraulisches
Hubmodul M enthält, mit dem zumindest die Senkbewegungen
des Hubzylinders elektrisch steuerbar sind. Das Hubmodul
M enthält eine Meßblende B und stromab der Meßblende B eine
Druckwaage W. Die Stellung der Meßblende B wird über ein Vorsteuerventil
V eingestellt, das mittels eines Proportionalmagneten
9 in Abhängigkeit von dessen Bestromung aus der dargestellten
Stellung gegen eine Feder verstellbar ist.A hydro consumer, not shown, e.g. the lifting cylinder
a forklift, is controlled from a work line H,
via a
Die Positionen der Meßblende B und der Druckwaage W können in
der Ablaßleitung 3 auch vertauscht Werden. Ferner ist es möglich,
die Meßblende B direkt durch den Proportionalmagneten 9
zu betätigen. In jedem Fall muß dafür gesorgt sein, daß die
die Schließ- und die Öffnungsseite der Druckwaage beaufschlagenden
Steuerleitungen der Druckwaage die Druckdifferenz aufgeben,
die über die Meßblende B eingestellt ist.The positions of the orifice plate B and the pressure compensator W can be in
the
Bei der gezeigten Ausführungsform zweigt von der Ablaßleitung
3 eine Steuerleitung 4 ab, die zur Schließseite der einen Regelkolben
10 enthaltenden Druckwaage W führt. Von der Steuerleitung
4 zweigt eine Steuerleitung 5 zu einem Anschluß des
Vorsteuerventils V ab. Zwischen der Meßblende B und der
Druckwaage W zweigt von der Ablaßleitung 3 im Punkt 6 eine
Steuerleitung 7 ab, die einerseits zur Schließseite der Meßblende
B und zur Öffnungsseite der Druckwaage W und andererseits
zu einem zweiten Anschluß des Vorsteuerventils V sowie
zu dessen dem Proportionalmagneten 9 zugewandter Vorsteuerseite
führt. Ein gegenüberliegender Anschluß des Vorsteuerventils
V ist über eine weitere Steuerleitung 8 mit der Öffnungsseite
der Meßblende B verbunden, wobei in der Steuerleitung
8 eine Dämpfdrossel D1 vorgesehen sein kann. In der Steuerleitung
4 ist eine Dämpfdrossel D2 vorgesehen, die in
Schließrichtung der Druckwaage W durch ein paralleles Rückschlagventil
R umgehbar ist. Ferner ist (punktiert angedeutet)
ein die Dämpfdrossel D2 und das Rückschlagventil umgehender
Beipaßkanal Y vorgesehen, auf den im Detail bei der
Erläuterung der Fig. 2 eingegangen werden wird.In the embodiment shown branches from the
Die Druckwaage wird in Öffnungsrichtung durch eine Regelfeder
11 beaufschlagt. Die Dämpfdrossel D2 dämpft Druckschwankungen
und die Öffnungsbewegung des Regelkolbens 10 bzw. der Druckwaage
W bei sperrendem Rückschlagventil R. Das Rückschlagventil
R öffnet, sobald die Druckwaage zu schließen ist, so daß
dann die Dämpfdrossel D2 umgangen wird.The pressure compensator is opened in the opening direction by a
Gemäß Fig. 2 ist der Regelkolben 10 der Druckwaage W in einer
Gehäusebohrung 22 eines Gehäuses 12 verschiebbar geführt, das
auch die Meßblende B enthält. Der Regelkolben 10 ist mit einer
kleinen Passung von nur wenigen Mikron in die Gehäusebohrung
22 eingepaßt und arbeitet mit positiver Überdeckung, um
in der in der oberen Hälfte der Figur gezeigten Schließendstellung
die Mündung der Ablaßleitung 3 zuverlässig gegenüber
der Mündung des Astes 3' der Ablaßleitung abzudichten. Die
positive Überdeckung kann zwischen 2 und 10 mm, vorzugsweise
zwischen 2 und 2,5 mm betragen. Der Regelkolben 10 weist eine
Umfangsnut 25 mit einer Flanke 26 auf, die blendenartig mit
den Mündungen der Ablaßleitung 3 und des Astes 3' der Ablaßleitung
zusammenarbeitet. Angrenzend an die Flanke 26 ist eine
Dichtzone am Regelkolben 10 vorgesehen, die mit der Wand
der Gehäusebohrung 22 zusammenwirkt. Die Regelfeder 11 beaufschlagt
den Regelkolben 10 auf derselben Seite wie der Druck
in der Steuerleitung 7, und zwar entgegengesetzt zum Druck in
einer Steuerkammer 23 am rechtseitigen Ende der Gehäusebohrung
22. Die Steuerleitung 4 bzw. ihr Ast 4' mündet in die
Kammer 23. Ferner ist eine Beipaßleitung Y vorgesehen, deren
Mündung 28 in der Wand der Gehäusebohrung 37 derart angeordnet
ist, daß sie mit einer Absperrkante 27 des Regelkolbens
10 sowie mit einer an die Absperrkante 27 angrenzenden Dichtfläche
37 zusammenarbeitet. Der Beipaßkanal Y umgeht eine
Aufnahmebohrung 13 im Gehäuse 12 und führt von der Steuerkammer
23 direkt zur Steuerleitung 4. In die Aufnahmebohrung 13
ist ein Einschraubventileinsatz E mit einem Einschraubgehäuse
14 eingeschraubt, das einen Ventilsitz 15 enthält. Im Einschraubgehäuse
14 ist ein kapselförmiges Ventilelement 17
enthalten, das mit dem Ventilsitz 15 als Rückschlagventil R
zusammenarbeitet und durch eine Ventilfeder 29 in Schließrichtung
beaufschlagt wird. Das Ventilelement 17 ist hohl
ausgebildet und enthält einen längsdurchgehenden Strömungsweg,
der in den Ventilsitz 15 mündet. Im Ventilelement 17 ist
die Dämpfdrossel D2, hier in Form einer Kaskadendrossel 18,
enthalten. Das Einschraubgehäuse 14 weist einen weiteren
Längsdurchgang 16 und einen Querkanal 20 auf. Auf das Einschraubgehäuse
14 ist eine Kappe 21 aufgeschraubt, die gegenüber
dem Gehäuse 12 abdichtet und den Strömungsweg zum bzw.
vom Ast 4' des Steuerkanals schließt. Im Einschraubgehäuse 14
ist eine Drehhilfe 19 eingeformt. Die Kappe 21 besitzt einen
Sechskantkopf.2, the
Die Mündung 28 des Beipaßkanals Y ist so angeordnet, daß sie
in der in Fig. 2, obere Hälfte, gezeigten Schließendstellung
des Regelkolbens 10 frei ist und die Steuerkammer 23 unter
Umgehung des Rückschlagventils R und der Dämpfdrossel D2 direkt
mit der Steuerleitung 4 verbindet. Bei einer Bewegung
des Regelkolbens 10 aus der dargestellten Schließendstellung
in Richtung zu einer anfänglichen Öffnungsstellung bleibt die
Mündung 28 zunächst frei, bis die Flanke 26 sich mit der Mündung
des Astes 3' der Steuerleitung überschneidet und eine
Verbindung herstellt. Dann, d.h. kurz davor, kurz danach oder
exakt zu diesem Zeitpunkt, wird mittels der Absperrkante 27
und der Dichtfläche 37 die Mündung 28 verschlossen und der
Beipaßkanal passiviert. Bei einer weiteren Bewegung des Regelkolbens
10 in Richtung auf die volle Öffnungsstellung
(untere Hälfte von Fig. 2) bleibt der Beipaßkanal Y verschlossen;
das Steuerdruckmittel muß den Weg über die Dämpfdrossel
D2 nehmen.The
Die Meßblende B weist einen Blendenkolben 31 auf, der in einer
Gehäusebohrung 30 axial verstellbar ist, und zwar nach
Maßgabe der Drücke in den Steuerleitungen 7 und 8 und einer
Feder 32. Eine Einstellschraube 33 dient zum Einstellen der
Grenzmenge der Meßblende B.The orifice plate B has an
Bei der Ausführungsform gemäß Fig. 3 ist die Dämpfdrossel D2
eine sogenannte Gewindedrossel, gebildet durch ineinandergreifende
Gewinde 35 am Einschraubgehäuse 34 des Einschraubventileinsatzes
E und dem Gewinde 36 der Aufnahmebohrung. Im
Einschraubgehäuse 34 ist der Ventilsitz 15 vorgesehen, mit
dem ein beispielsweise als Kugel ausgebildetes Ventilelement
18 zusammenarbeitet, das von einer Feder 29 in Schließrichtung
belastet wird. Der weitere Aufbau des Einschraubventileinsatzes
E entspricht dem von Fig. 2. Der Beipaßkanal Y umgeht
auch hier das Rückschlagventil und die Dämpfdrossel D2.In the embodiment according to FIG. 3, the damping throttle is D2
a so-called thread choke, formed by interlocking
Anstelle einer Gewindedrossel oder der gezeigten Kaskadendrossel könnte auch eine andere Drossel, z.B. mit einem verstellbaren Drosselelement, verwendet werden.Instead of a thread choke or the cascade choke shown could also be another choke, e.g. with an adjustable Throttle element can be used.
Die Kaskadendrossel 18 der Fig. 2 besteht aus einer Vielzahl von Kaskadenelementen, die als Blendenplättchen ausgebildet und zu einem Paket zusammengefaßt sind, wobei die einzelnen Blendenplättchen durch dazwischengelegte Distanzringe voneinander beabstandet sind. Jedes Blendenplättchen enthält eine kleine Durchgangsbohrung. Die ersten Blendenplättchen des Pakets können mehrere kleine Durchgangsbohrungen aufweisen, um als Filter für Verunreinigungen zu dienen.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.
Claims (12)
- Electrohydraulic lifting module (M) for a hydraulic load which can be acted on on one side from a pressure source (P) via a working line (H), in particular a lifting cylinder, having a two-way volume controller (B, W) in a discharge line (3') that is arranged between the working line (H) and a return line (R), the two-way volume controller having a metering orifice (B) that can be adjusted by means of a proportional magnet, and a pressure balance (W) that is hydraulically connected to the stacker and has a control piston (10), the latter being acted on on the closing side from a first control line (4), counter to a control spring (11), and being acted on on the opening side by the control spring (11) and from a second control line (7), and having a damping restrictor (D2) for at least the opening stroke of the control piston (10) of the pressure balance (W), characterized in that the control chamber (23) on the closing side of the pressure balance (W) is connected to the first control line (4) via a bypass duct (Y), in that the bypass duct (Y) bypasses the damping restrictor (D2), and in that the opening (28) of the bypass duct (Y) in one wall of the control chamber is arranged in such a way that it is clear during a stroke of the control piston (10) from its closed end position as far as approximately an initial opening position of the pressure balance (W), and is blocked off by the control piston (10) during the further opening stroke of the control piston from approximately the initial opening position.
- Lifting module according to Claim 1, characterized in that an intermediate axial spacing (positive overlap) in relation to the control piston (10) is provided between an inlet opening and an outlet opening of the discharge line (3, 3'), and in that, in the closed end position of the control piston (10), the distance (viewed in the opening stroke direction) between a shut-off edge (27) of the control piston (10) and the edge, located behind in this stroke direction, of the opening (28) of the bypass duct (27) approximately corresponds to the intermediate spacing.
- Lifting module according to Claims 1 and 2, characterized in that the control piston (10) has, adjacent to the shut-off edge (27), a sealing face (37) for shutting off the opening (28) of the bypass duct (Y).
- Lifting module according to Claim 1, characterized in that the bypass duct (Y) has a smaller cross-section than the control line (4, 4'), for example a diameter of about 1 mm as compared with a diameter of the control line of about 4 mm.
- Lifting module according to Claim 1, characterized in that the damping restrictor (D2, D1) is a cascade restrictor (18) with a multiplicity of cascade elements.
- Lifting module according to Claim 1, characterized in that the damping restrictor (D2, D1) is a threaded restrictor, in which a restricted flow path is formed between interengaging turns of internal and external threads (35, 36).
- Lifting module according to Claim 1, characterized in that the damping restrictor (D1, D2) has an adjustable restrictor element.
- Lifting module according to Claims 1, 5 and 6, characterized in that the damping restrictor (D2) can be bypassed in the flow direction towards the closing side of the pressure balance (W) via a non-return valve (R), and in that the damping restrictor (D2) is arranged in the non-return valve (R).
- Lifting module according to Claims 1, 5, 6 and 8, characterized in that the non-return valve (R) is a screw-in valve insert (E), which is screwed into a receiving bore (13), which intercepts the control line (4, 4'), in a housing (12) of at least the pressure balance (W), and has a spring-loaded valve element (17) and a valve seat (15).
- Lifting module according to Claims 1, 6 and 9, characterized in that the screw-in valve insert (E) has an externally threaded section (35), which is screwed into an internal thread (36) of the receiving bore (13) and, with the latter section, forms the threaded restrictor.
- Lifting module according to Claims 1, 5 and 9, characterized in that the valve element (17) of the non-return valve (R) is constructed as a capsule with a flow path opening into the valve seat (15), and in that the cascade restrictor (18) is arranged in the capsule.
- Lifting module according to Claims 9 to 11, characterized in that a cap (21), which seals against the housing (12) is screwed onto the screw-in valve insert (E), which projects from the receiving bore (13).
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE29508394U DE29508394U1 (en) | 1995-05-19 | 1995-05-19 | Electro-hydraulic lifting module |
DE29508394U | 1995-05-19 |
Publications (2)
Publication Number | Publication Date |
---|---|
EP0743459A1 EP0743459A1 (en) | 1996-11-20 |
EP0743459B1 true EP0743459B1 (en) | 1998-08-12 |
Family
ID=8008337
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP96106917A Expired - Lifetime EP0743459B1 (en) | 1995-05-19 | 1996-05-02 | Electrohydraulic lifting device |
Country Status (5)
Country | Link |
---|---|
EP (1) | EP0743459B1 (en) |
AT (1) | ATE169723T1 (en) |
DE (2) | DE29508394U1 (en) |
DK (1) | DK0743459T3 (en) |
ES (1) | ES2122741T3 (en) |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE19716442A1 (en) * | 1997-04-20 | 1998-10-22 | Eckehart Schulze | Hydraulic installation on a forklift vehicle |
Family Cites Families (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE3171757D1 (en) * | 1981-01-16 | 1985-09-19 | Heilmeier & Weinlein | Electromagnetically operated multiple-way hydraulic valve |
DE3705170C1 (en) * | 1987-02-18 | 1988-08-18 | Heilmeier & Weinlein | Hydraulic control device |
DE4239321C2 (en) * | 1992-11-23 | 1995-11-09 | Heilmeier & Weinlein | Electro-hydraulic lifting module |
-
1995
- 1995-05-19 DE DE29508394U patent/DE29508394U1/en not_active Expired - Lifetime
-
1996
- 1996-05-02 DE DE59600416T patent/DE59600416D1/en not_active Expired - Lifetime
- 1996-05-02 EP EP96106917A patent/EP0743459B1/en not_active Expired - Lifetime
- 1996-05-02 AT AT96106917T patent/ATE169723T1/en not_active IP Right Cessation
- 1996-05-02 DK DK96106917T patent/DK0743459T3/en active
- 1996-05-02 ES ES96106917T patent/ES2122741T3/en not_active Expired - Lifetime
Also Published As
Publication number | Publication date |
---|---|
ES2122741T3 (en) | 1998-12-16 |
DK0743459T3 (en) | 1999-05-17 |
DE29508394U1 (en) | 1995-08-03 |
DE59600416D1 (en) | 1998-09-17 |
EP0743459A1 (en) | 1996-11-20 |
ATE169723T1 (en) | 1998-08-15 |
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