US3687011A - Control valve block for hydraulically operated elevators - Google Patents

Control valve block for hydraulically operated elevators Download PDF

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Publication number
US3687011A
US3687011A US30378A US3687011DA US3687011A US 3687011 A US3687011 A US 3687011A US 30378 A US30378 A US 30378A US 3687011D A US3687011D A US 3687011DA US 3687011 A US3687011 A US 3687011A
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United States
Prior art keywords
piston
control
conduit
precontrol
channel
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Expired - Lifetime
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US30378A
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English (en)
Inventor
Hubert Haussler
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.)
BERINGER HYDRAULIK GmbH
Beringer-Hydraulik R Beringer & Co
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BERINGER HYDRAULIK GmbH
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66B—ELEVATORS; ESCALATORS OR MOVING WALKWAYS
    • B66B1/00—Control systems of elevators in general
    • B66B1/24—Control systems with regulation, i.e. with retroactive action, for influencing travelling speed, acceleration, or deceleration
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66B—ELEVATORS; ESCALATORS OR MOVING WALKWAYS
    • B66B1/00—Control systems of elevators in general
    • B66B1/34—Details, e.g. call counting devices, data transmission from car to control system, devices giving information to the control system
    • B66B1/36—Means for stopping the cars, cages, or skips at predetermined levels
    • B66B1/40—Means for stopping the cars, cages, or skips at predetermined levels and for correct levelling at landings
    • B66B1/405—Means for stopping the cars, cages, or skips at predetermined levels and for correct levelling at landings for hydraulically actuated elevators

Definitions

  • ABSTRACT A control valve block assembly for hydraulically operated elevators or the like comprising a single pressure differential balance means for both directions of travel of the elevator, this pressure differential balance means incorporating a control piston.
  • Means define an intermediate channel communicating with the cylinder of the elevator drive unit, with said control piston maintaining in said intermediate channel the pressure deviating from the load pressure in the elevator cylinder by a constant amount.
  • Reversing piston means serve to determine the deviationof the pressure at the high side or the low side of such load pressure, depending upon the direction of travel of the elevator.
  • dosing piston means is provided which in its open position provides a flow communication from said pressure differential balance means to said cylinder and thus regulates the quantity of hydraulic fluid medium flowing to and from such cylinder.
  • Two electromagnets are also'provided, eachof which is operatively coupled with one precontrol slide means, and when energized actuates its associated precontrol slide means, one such precontrol slide means directly controlling the position of said control piston and the other precontrol slide means directly controlling the position of said dosing piston means,
  • the present invention relates to a new and improved control valve block assembly for hydraulically actuated elevators or lifts.
  • control blocks or units have become known in which for the upward and downward travel a respective separate control valve is required. This solution is equally expensive and requires a great deal of space.
  • Another, more specific'object of the present invention relates to an improved hydraulic control system for elevators or lifts which is relatively simple in construction, extremely reliable in operation, provides for accurate control of the elevator-throughout various speed modes, and effectively over comes the aforementioned disadvantages associated with the prior art constructions, while fulfilling the requirements placed upon devices of this type as heretofore enumerated.
  • the inventive control valve block or unit for hydraulically operated elevators or lifts is generally manifested by the features that there is provided only a single pressure differential balance for both directions of travel, the control piston of which maintains the pressure in an intermediate channel communicating with the cylinder of the elevator drive unit, which pressure deviates by a constant amount from the load pressure in such cylinder. This deviation towards the high side or the low side, depending upon the direction of travel of the elevator, being determined by a switching or reversing piston.
  • the invention contemplates the provision of a dosing piston member constructed as a sealing seat valve which in open position provides a communication of the pressure differential balance to the cylinder, and thus quantitatively controls the hydraulic fluid flowing to and from, respectively, this cylinder.
  • the invention contemplates the provision of two electromagnets which in their energized state actuate a respective precontrol slide, wherein one such precontrol slide directly controls the position of the control or regulating piston and the other precontrol slide directly controls the position of the dosing piston member.
  • FIG. 1 is a schematic, partially sectional view, of a preferred embodiment of inventive control valve block or unit
  • FIG. 2 is a known motion or travel graph for an elevator in which, however, there has additionally been added the momentary operational duration of the hydraulic pump and the control magnets.
  • the inventive control valve block or unit is formed of two components, namely an upper component and a lower component, which can be separated from one another.
  • the lower component constitutes the main control component, directly controls the through-flowing oil, and is designed for a predetermined quantity of oil.
  • this main control component is then dimensioned appropriately different.
  • the upper component constitutes the precontrol valve. It is operated with a small, practically constant quantity of oil, thus actuates the main control component and can therefore be used for different structural sizes of such main control component, and with which it can be freely exchanged.
  • the precontrol valve under consideration supports the electromagnets 9 and 10 which, during travel of the elevator or lift, actuate switches arranged in the elevator shaft and, therefore, triggers the control functions of the entire control valve block or unit.
  • control piston 5 is subjected at one side or face (in this instance the bottom or lower face) to the pressure prevailing in the intermediate channel 3, this pressure being transmitted via the bore 4 to this lower face of the aforementioned piston 5.
  • the other upper face of the piston 5 is subjected to the action of the pressure or compression spring 6 (when the installation is out of operation, that is to say when only the oil pump is in operation, yet magnets 9 and 10 are still not energized) as well as additionally (after energization of the magnets) to the action of the load pressure of the elevator.
  • the balancing of these forces brings about a displacement of the control piston 5 in the upward direction, so that oil, with a load-dependent pressure gradient, can flow from the intermediate channel 3 past the control edge 7 into the return flow channel 8.
  • This pressure differential balance therefore resides in maintaining a pressure inthe intermediate channel 3 which, when the elevator is moving upwards, is at a constant value above the load pressure in the cylinder of the elevator drive unit, and during downward travel of the elevator is at a constant value below the load pressure in such cylinder of such elevator drive unit.
  • This function of such pressure difierential balance is achieved will be more fully explained hereinafter under the section dealing with the operation of the invention. Yet, it is of significance to here remark that for both directions of travel of the elevator a single pressure differential balance is sufficient.
  • reference numeral 20 designates a dosing piston member which is subjected to the action or a compression or pressure spring 21.
  • the function of this dosing piston member 20 is to provide operable communication between the consumer (elevator cylinder) and the intermediate channel 3, and further to regulate, that is to 'say, to maintain at an adjustable value, the throughflowing quantity of oil, and finally, to hennetically seal the consumer conduit when the elevator or lift is stationary so that such does not slowly drop.
  • the piston member 20 is advantageously constructedas a cone seat valve which bears against an appropriately configured valve seat 56.
  • the dosing piston member 20 is actuated by a piston 16 which is controlled via a conduit 14 by. the magnet 10, whereas its opposite side is coupled via a conduit 17 directly with the return flow channel 8. So that this actuation need not occur against the full load pressure,
  • valve member 19' which initially relieves the face of the dosing piston member 21 situated opposite the piston 16, so that there is only acting upon this dosing piston the force of the spring member 21.
  • This unit embodies both of the electromagnets 9 and 10 equipped with a respective precontrol slide or spool 22 and 11 operably coupled therewith.
  • the slide member 1 1 is coupled via the conduit 12 with the intermediate channel 3 and via the conduit 14 with the actuation piston member 16.
  • the magnet 10 is deenergized, this communication is interrupted and instead of such, there is obtained a communication of the conduit 14 with the return flow channel 8 through the agency of conduit 51.
  • the slide member 22 is connected, on the one hand, via a conduit 25 with the elevator cylinder 102 and, on
  • conduits 27 and 30 via the conduits 27 and 30 with a control piston member 33 and, therefore, indirectly (through the agency of an annular channel 31, an annular compartment 36 and a conduit 37) with the compression spring side-face of the control piston 5.
  • the control piston 5 When the magnet 9 is energized the control piston 5 is positionally influenced by virtue of the pressure prevailing in the elevator or lift cylinder.
  • the slide member 22 Under the action of a spring, is displaced such that the conduits 27 and 30 are likewise operably coupled with the return flow channel 8, and specifically, through the agency of a channel 55.
  • a reversing piston 39 constituting part of the precontrol valve unit is a reversing piston 39, by means of which it is possible to utilize a single pressure differential balance 5, 6 for both directions of travel of the elevator.
  • This reversing piston is subjected to the action of a spring member 41 at one face thereof. At the other face there opens a conduit 40 leading from the pump connection 1. If the pump 100 is in operation, then, the pump pressure acts upon this face and displaces the piston member 39 against the action of the spring 41. This influences the pre-biasing of a spring 34 and therefore indirectly the position of the previously mentioned control piston 33 bearing at one face against this spring member 34.
  • the piston member 33 is coupled with different channels 30, 32, 37 and 45 and possesses the previously mentioned annular compartment 36 by means of which, depending upon the position of the piston, individual channels can be operatively communicated with one another in flow relationship.
  • a pressure gradient or drop which in magnitude is dependent upon the position of the annular compartment 36.
  • the armature of the magnet 10 pushes the precontrol slide 11 downwards and thus connects the intermediate channel 3 through the agency of the control conduit 12 and the sinter filter 13 with the control channel 14. From this location the pressurized oil arrives via an adjustable throttle 15 beneath the actuation piston member 16. Since the upper surface or face of this piston communicates via the conduit 17 with the return, it is displaced upwards, so that initially the ball check valve 19 is opened via the plunger 18. Consequently, the upper face of the dosing piston member 20, loaded by the spring member 21 and the pressure in the elevator cylinder, communicates with the return.
  • the cone check valve 24 is opened, so that the oil which is under pressure can flow out of the cylinder 102 via the control conduit 25 and the sinter filter 26 into the control conduit 27. From this location the pressurized oil moves through the conduit 28 both to the lower face of the piston 29 as well as via the conduit 30 into the annular or ring-shaped channel 31 which is in flow communication via the conduit 32 with the lower surface or face of the control piston 33.
  • this piston member Since the upper surface or face of this piston is initially only loaded by the spring member 34, this piston member is displaced upwards and allows pressurized oil to flow via the control edge 35 into the annular com- 6, causes the piston member 5 to assume an intermediate position in which it throttles the oil flow at the control edge 7 to such an extent that the pressure in the intermediate channel 3 is greater by a certain difference than the momentary pressure in the cylinder.
  • This constant pressure differential at the dosing piston 20 now causes a flow ina direction to the cylinder which is only dependent upon the position of the dosing piston 20 and no longer upon the pressure in the cylinder.
  • the pressure differential at the dosing piston member 20 is adjustable between, for instance, 0-4 kp/cm2 by means of the impact or stop screw member 38, so that with the same open cross section there can be controlled different throughflow quantities.
  • the impact screw member 38 limits the stroke of the reversing piston 39 which is upwardly displaced against the force of the spring member 41'by the pump pressure in the connection 1 via the control conduit 40, since the spring compartment is coupled via the conduit 42 with the return.
  • the position of the reversing piston 39 influences the force of the spring member 34 acting upon the control piston 33, which in turn results in enabling a change in the pressure gradient or drop between the annular channel 31 and the annular compartment 36. Since the pressure in the annular compartment 36 acts via the bore 43 upon the upper face of the control piston 33, whereas the pressure in the annular channel 31 acts upon the lower face of control piston 33 through the agency of the bore 32, the piston member 33 is adjusted in its equilibrium position when the pressure in the annular compartment 36 is smaller by the force of the spring 34 than the load pressure in the annular channel 31. The reduced load pressure acts via the control conduit 37, together with the force of the spring member 6, upon the upper face of the control piston 5.
  • the opening velocity of the control piston 5 can be influenced by means of the impact or stop screw 44,
  • the spring member 50 displaces the precontrol slide 11 upwards into the illustrated position, whereby the control conduit '14 is coupled with the return flow conduit 51.
  • the spring 21 presses the dosing piston member 20 together with the actuation piston member 16 downwards, so that control oil is displaced via the check valve'52 and the throttle 53 into the return. Since the dosing piston 20 is completely pressure equalized there is provided a continuous deceleration of the elevator independently of the load pressure, which can be adjusted by means of the throttle 53. However, the elevator is decelerated only until the actuation piston 16 impacts against the piston member 29 which is pressed by means of the load pressure in the control conduit 28 against the collar of the impact screw 54.
  • the pump can therefore run out unloaded which does not have any influence upon the stopping accuracy of the elevator. Due to the leakage in the annular gap 57, the load pressure at the upper face of the dosing piston 20 builds up and tightly presses such as well as the ball 19 against its seat. Since the check valve 24 is also again closed, no leakage oil whatsoever can escape any longer out of the cylinder compartment.
  • the check valve 58 is only installed for security reasons, in order that the dosing piston 20 does not remain open, or opens if for some reason the magnet 9 is deenergized which would result in the elevator no longer provides any resistance.
  • the operation during downward travel of the elevator or lift is essentially the same as during upward travel thereof and differs only in the following manner: Since the pump during downward travel is not operational, the conduit 40 is without pressure. Consequently, the reversing piston 39 is pressed by means of the spring 41 against the impact screw 59, resulting in ,a larger prebiasing of the spring 34.
  • the pressure drop between the control conduit means 30 and 37 can thus be regulated by the impact screw 59 from 4- kp/cm2 up to, for instance, 8 kp/cm2.
  • the downward travel of the lift occurs, therefore, likewise load-independent and braked by means of the control piston 5, whereas the velocity is controlled by the'dosing piston 20.
  • the magnet 10 is deenergized, so that the control conduit 14 is coupled with the return flow conduit 51 which opens into the return flow channel 8.
  • the return flow therefore flows past the throttles l5 and 53 and is consequently dependent upon their positions, that is to say, from the throttle cross-section, and furthermore, however, also upon the viscosity of the return flowing liquid. Changes in the viscosity therefore also result in changes in the deceleration.
  • a control valve block assembly for hydraulically operated elevators or the like for the load-independent raising and lowering thereof and employing electromagnetic triggering of the control operation comprising an elevator drive cylinder unit, a hydraulic pump for a fluid medium and a return flow tank provided for said control valve block assembly, a single pressure differential balance means for both directions of travel of the elevator, said pressure differential balance means incorporating a control piston, means defining an intermediate channel communicating with said cylinder of the elevator drive cylinderunit, said control piston being located in flow communication with said intermediate channel and maintaining the pressure in said intermediate channel at a level deviating from the load pressure in the elevator cylinder by a constant amount, reversing piston means cooperating with said pressure differential balance means for determining the deviation ofsaid pressure to the high side or the low side depending upon the direction of travel of said elevator,.
  • dosing piston means constructed as a sealing seat valve unit which in its open position provides a flow communication from said pressure differential balance means to said cylinder and thus regulates the quantity of hydraulic fluid medium flowing to and from such cylinder, two precontrol slide valve means, two electromagnets each of which is operatively coupled with one of said precontrol slide valve means and when energized actuates its associated precontrol slide valve means, fluid conduit means provided for said precontrol slide valve means and said dosing piston means, one such precontrol slide valve means directly controlling the position of said control piston and the other precontrol slide valve means directly controlling the position of said dosing piston means, spring means acting upon said reversing piston means and an adjustable impact screw cooperating with said reversing piston means, a conduit communicating said pump with said reversing piston means, said reversing piston means during operation of said pump being displaced in one direction against the action of said spring means by virtue of the pressure prevailing in said conduit, and when said pump is inoperable and said conduit is without pressure said reversing piston means being displaced under the
  • control edge-means provided for said I control piston member, an annular compartment communicating via said control edge means said still further conduit with said further conduit leading to said control piston of said pressure differential balance means, the throughflow cross-section at the location of this control edge means and therefore the prevailing pressure drop being dependent upon the position of said control piston member determined by the pressure in said one branch line and the pre-bias of said spring acting upon said control piston member.

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  • Engineering & Computer Science (AREA)
  • Automation & Control Theory (AREA)
  • Computer Networks & Wireless Communication (AREA)
  • Types And Forms Of Lifts (AREA)
  • Fluid-Pressure Circuits (AREA)
US30378A 1969-04-25 1970-04-21 Control valve block for hydraulically operated elevators Expired - Lifetime US3687011A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CH633869A CH487063A (de) 1969-04-25 1969-04-25 Steuerventilblock für hydraulisch betriebene Aufzüge

Publications (1)

Publication Number Publication Date
US3687011A true US3687011A (en) 1972-08-29

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US30378A Expired - Lifetime US3687011A (en) 1969-04-25 1970-04-21 Control valve block for hydraulically operated elevators

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US (1) US3687011A (enrdf_load_stackoverflow)
AT (1) AT302573B (enrdf_load_stackoverflow)
CH (1) CH487063A (enrdf_load_stackoverflow)
DE (1) DE2018512C3 (enrdf_load_stackoverflow)
GB (1) GB1289883A (enrdf_load_stackoverflow)
SE (1) SE367172B (enrdf_load_stackoverflow)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0265729A3 (en) * 1986-10-17 1989-05-03 Cemcolift, Inc. Self-adjusting control valve for elevators

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3434014A1 (de) * 1984-09-15 1986-03-20 Beringer-Hydraulik GmbH, Neuheim, Zug Hydraulische steuerung
FI71710C (fi) * 1985-04-30 1987-02-09 Pentti Rita Elektriskt styrd ventilanordning.
FI874147A0 (fi) * 1987-09-22 1987-09-22 Pentti Rita Ventilanordning.

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2737197A (en) * 1950-05-31 1956-03-06 Dover Corp Hydraulic control apparatus
US3120880A (en) * 1960-12-23 1964-02-11 Dover Corp Hydraulic drive and control for elevators
DE1268801B (de) * 1964-02-08 1968-05-22 Erich Herion Druckmittelsteuerung eines Aufzugs
DE1431063A1 (de) * 1964-04-23 1968-11-28 Rexroth Gmbh G L Steuergeraet fuer eine hydraulische Kolben-Zylinder-Einheit,insbesondere an einem Aufzug
US3438398A (en) * 1967-04-10 1969-04-15 Esco Elevators Inc Hydraulic elevator control systems
US3508468A (en) * 1968-04-24 1970-04-28 Armor Elevator Co Inc Hydraulic elevator control valve

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2737197A (en) * 1950-05-31 1956-03-06 Dover Corp Hydraulic control apparatus
US3120880A (en) * 1960-12-23 1964-02-11 Dover Corp Hydraulic drive and control for elevators
DE1268801B (de) * 1964-02-08 1968-05-22 Erich Herion Druckmittelsteuerung eines Aufzugs
DE1431063A1 (de) * 1964-04-23 1968-11-28 Rexroth Gmbh G L Steuergeraet fuer eine hydraulische Kolben-Zylinder-Einheit,insbesondere an einem Aufzug
US3438398A (en) * 1967-04-10 1969-04-15 Esco Elevators Inc Hydraulic elevator control systems
US3508468A (en) * 1968-04-24 1970-04-28 Armor Elevator Co Inc Hydraulic elevator control valve

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0265729A3 (en) * 1986-10-17 1989-05-03 Cemcolift, Inc. Self-adjusting control valve for elevators

Also Published As

Publication number Publication date
CH487063A (de) 1970-03-15
DE2018512A1 (de) 1970-11-12
GB1289883A (enrdf_load_stackoverflow) 1972-09-20
SE367172B (enrdf_load_stackoverflow) 1974-05-20
DE2018512B2 (de) 1980-06-19
AT302573B (de) 1972-10-25
DE2018512C3 (de) 1981-02-26

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