US3300190A - Control arrangement - Google Patents

Control arrangement Download PDF

Info

Publication number
US3300190A
US3300190A US508195A US50819565A US3300190A US 3300190 A US3300190 A US 3300190A US 508195 A US508195 A US 508195A US 50819565 A US50819565 A US 50819565A US 3300190 A US3300190 A US 3300190A
Authority
US
United States
Prior art keywords
cylinder
conduit
pressure
band
brake
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
US508195A
Other languages
English (en)
Inventor
Blase Helmut
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.)
Rheinstahl Union Brueckenbau AG
Original Assignee
Rheinstahl Union Brueckenbau AG
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Rheinstahl Union Brueckenbau AG filed Critical Rheinstahl Union Brueckenbau AG
Application granted granted Critical
Publication of US3300190A publication Critical patent/US3300190A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66D—CAPSTANS; WINCHES; TACKLES, e.g. PULLEY BLOCKS; HOISTS
    • B66D1/00—Rope, cable, or chain winding mechanisms; Capstans
    • B66D1/02—Driving gear
    • B66D1/14—Power transmissions between power sources and drums or barrels
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66D—CAPSTANS; WINCHES; TACKLES, e.g. PULLEY BLOCKS; HOISTS
    • B66D1/00—Rope, cable, or chain winding mechanisms; Capstans
    • B66D1/02—Driving gear
    • B66D1/08—Driving gear incorporating fluid motors
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66D—CAPSTANS; WINCHES; TACKLES, e.g. PULLEY BLOCKS; HOISTS
    • B66D5/00—Braking or detent devices characterised by application to lifting or hoisting gear, e.g. for controlling the lowering of loads
    • B66D5/02—Crane, lift hoist, or winch brakes operating on drums, barrels, or ropes
    • B66D5/24—Operating devices
    • B66D5/26—Operating devices pneumatic or hydraulic
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66D—CAPSTANS; WINCHES; TACKLES, e.g. PULLEY BLOCKS; HOISTS
    • B66D2700/00—Capstans, winches or hoists
    • B66D2700/01—Winches, capstans or pivots
    • B66D2700/0125—Motor operated winches
    • B66D2700/0133—Fluid actuated
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66D—CAPSTANS; WINCHES; TACKLES, e.g. PULLEY BLOCKS; HOISTS
    • B66D2700/00—Capstans, winches or hoists
    • B66D2700/01—Winches, capstans or pivots
    • B66D2700/0125—Motor operated winches
    • B66D2700/0158—Hydraulically controlled couplings or gearings
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66D—CAPSTANS; WINCHES; TACKLES, e.g. PULLEY BLOCKS; HOISTS
    • B66D2700/00—Capstans, winches or hoists
    • B66D2700/03—Mechanisms with latches or braking devices in general for capstans, hoists or similar devices as well as braking devices actuated electrically or by fluid under pressure
    • B66D2700/035—Fluid operated braking devices

Definitions

  • the present invention relates to a fluid-operated control arrangement. More particularly, the invention relates to a ⁇ cont-rol arrangement which is especially suited to regulate the operation of one or more Winches on mobile cranes and similar machines. Such Winches are used for lifting or lowering of loads as Well as for operating a shovel, a dragline bucket or an analogous material moving or excavating element. v
  • a Winch having, for example, two cable drums is controlled by means of two actuating levers, one for each cable drum.
  • the customary pedals or triadles are then blocked or removed and the brakes which control lunwinding of cables from the respective cable drums are applied by means of springs.
  • the bias of the springs is overcome by hydraulic pressure iluid, i.e., the brakes are applied mechanically and are released hydraulically.
  • the winch is controlled by a pedal and by an actuating lever for each cable drum.
  • the brakes are applied mechanically yand are released by means of a hydraulic pressure iluid in the same way as in the first setup.
  • Each cable drum of the winch is controlled by a separate actuating lever and by a separate pedal, and the brake is applied by hydraulic pressure against spring action.
  • Each cable drum of a multiple-drum Winch is operated independently of the other drum or drums according to the setup (a), (b) or (c). y
  • the setup (a) is utilized when the Winch is used for lowering or lifting of loads.
  • the setup (b) is used for lifting and lowering or for excavating Work.
  • the setup (c) is intended for use in excavating work, and the set-up (d) is resorted to in special cases.
  • th-e setup (a) the overlapping of control operations involving coupling and release of the lowering brake or applying the planetary brake and releasing the lowering brake is effected by mechanical controls.
  • the maximum load Prior to beginning of an operation in accordance with a selected setup, the maximum load must be shortly lifted lto test the control arrangement and to determine Whether or not -the load 'will begin to descend kwith the actuating lever is moved between its end positions.
  • the customary control cams which are mounted in the control stand and serve to regulate the sequence of operations must be readjusted prior Vto starting With the operation according to a selected setup.
  • a conventional control arrangement can operate properly only if the vehicle which mounts the winch or Winches carries an ample supply of spare parts or attachments, such as are needed in certain (fbut not all) setups. This involves -additional problems, especially when the vehicle is used on rough terrain, for example, at construction sites, in excavations and the like,
  • Another object of the invention is to provide a crane of the just outlined characteristics vwherein the conversion from one type to another type of setup may be effected Without necessitating removal ⁇ or attachment of component parts so that the conveyance on which the machine is mounted need not carry a supply of spare parts such ias are used in one but not in all setups.
  • a further object ofthe invention is to provide a novel hydraulic and/or pneumatic vcontrol arrangement which may be used to regulate the operation of various as-A semblies and devices in the improved crane.
  • An additional object of the invention is to provide a.
  • Another object of the invention is to provide .a novel mentioned control arrangement land can be used in lmobile cranes with one or more Winches.
  • a concomitant object of the invention is to provide a crane which meets all regulations regarding Vthe safety of its operation and which can be economically employed for excavating work, ⁇ which can be used with optimum eiiiciency foreach such type of 'Work :and which, to my knowledge, is the rst truly univers-al machine capable of safely, economically annd satisfactorily fulfilling all of the above ⁇ outlined objects.
  • one feature of my present invention resides in the provision of a machine which is particularly suited for use as a mobile crane.
  • the machine comprises a winch including a cable drum7 a brakin-g device for the cable drum comprising a brake drum operatively connected with the cable drum, a brake b-and surrounding the brake drum ⁇ and having a xed end portion and a second end portion, and an operating unit for moving the second end Aportion of the brake band toward and away from the rst end portion to thereby apply or disengage the brake band from the brake drum.
  • the operating unit comprises a double-acting cylinder coupled to the second end portion of the brake b and, fixed piston means received in the cylinder, spring means for normally biasing the cylinder in a direction to lapply the brake band, and releasable locking means ⁇ for the spring means.
  • the machine further comprises .a preferably hydraulic control arrangement for regulating the operating unit and including ya circuit having a pair of lfeed conduits connected with the cylinder of the operating unit, a source of pressure fluid installed in the circuit, actuating means for selectively operating the locking means, and control means for selectively admitting pressure fluid through the feed conduits so as to apply the brake band by the action of the spring means ywhen the locking means is idle, to disengage the brake band when one of the feed conduits admits pressure lluid into the cylinder of the operating uint, and to apply the brake band by fluid pressure when the other feed conduit admits fluid into the cylinder of the operating unit while the locking means is operative.
  • a preferably hydraulic control arrangement for regulating the operating unit and including ya circuit having a pair of lfeed conduits connected with the cylinder of the operating unit, a source of pressure fluid installed in the circuit, actuating means for selectively operating the locking means, and control means for selectively admitting pressure fluid through the feed conduits so as to apply the
  • FIG. l is a diagram showing a control arrangement which is constructed and assembled in accordance with a first embodiment of the present invention
  • FIG. 2 is a fragmentary perspective view of a winch which is controlled by the arrangement of FIG. l;
  • FIG. 3 is a diagram showing va portion of a modified control arrangement wherein one of the brake operating cylindersl shown in FIG. l is replaced by a storing receptacle;
  • FIG. 4 is an enlarged longitudinal sectional View of a brake operating unit which is shown in operative position in which the brake band is applied by means of a spring, ⁇ the section being taken in the direction of arrows as seen from the line IV-IV of FIG. 5;
  • FIG. 5 is a side elevational view of the unit as seen from the left-hand side of FIG. 4;
  • FIG. 6 illustrates the brake operating unit in ⁇ a dfferent position when the unit is ready to apply the brake band by hydraulic pressure
  • FIG. 7 is a fragmentary longitudinal section through a modied operating unit.
  • FIG. 8 is a diagram showing a third control arrangement.
  • the apparatus which is shown in FIGS. l and 2 comprises a rst operator-controlled actuating member in the form of a lever 1 which is fulcrumed .at 1a and resembles a balance beam.
  • This lever 1 is utilized to operate two signal or impulse transmitting cylinders 2 and 3 in such a way that the cylinder 2 is idle ⁇ when the cylinder 3 transmits a signal, or vice versa.
  • the apparatus further comprises a second operator-controlled actuating member in the form of Ia depressible pedal or treadle 4 which controls a third signal transmitting cylinder 5a laccommodating a differential piston 5.
  • There is a rst control valve 6 having an adjusting element 6a,
  • the winch comprises a cable drum or reel 10 for a length of corivoluted flexible cable 23.
  • the means ⁇ for driving the drum 10 includes Ia toothed spur gear 11, a first brake drurn 12 with a brake band 13 and a hydraulic clutch 14, and a motor (not shown) which can drive the cable drum 10 through the intermediary of the spur gear 11.
  • a planetary transmission 15 cooperates with a second brake drurn 16 and with a brake band 17 to lower the load which is suspended at the ⁇ free end of the cable 23.
  • the hydraulic circuit of the control arrangement comprises an oil tank 18 or an -analogous source of hydraulic fluid, a hydraulic pump 19 which draws vad from the tank 18, and a pressure tank 21.
  • a switchover valve 20 is provided in a Iirst conduit 2da which connects the tanks 18 and 21, and a one-way valve 22 is provided in a second conduit 22a which connects the conduit 20a with the valve 20 and with the pressure side of the pump 19.
  • the valve 22 prevents return ow of compressed uid through the conduit 22a.
  • the operator pivots the actuating lever 1 in a counterclockwise direction, as viewed in FIG. l (see the arrow H), whereby the lever turns about the fulcrurn 1a and its upper motion transmitting pin 1b shifts the piston 2a in the signal generating cylinder 2 against the bias of a return spring 2b.
  • the pin lb is slidable in an elongated slot 2c provided in the piston rod 2d of the cylinder 2, but the spring 2b maintains the piston rod 2d in actual abutment with the pin 1b when the lever l is rocked in a counterclockwise direction.
  • the lower motion transmitting pin llc of the lever 1 slides in the elongated slot 3c of the lower piston rod 3d so that the piston 3a in the cylinder 3 remains idle.
  • the chamber 2e of the upper cylinder 2 is connected with a supply conduit 26 which receives oil from the tank 1S and, on depression of the piston 2a against the bias of the spring 2b, a certain quantity of oil is expelled' through a discharge conduit 2S communicating with a connecting conduit 25a and with one inlet of a reversible valve 27.
  • the fluid which is expelled from the chamber 2e of the cylinder 2 ows through the conduits 25, 25a and into the working chamber of a cylinder 24 forming part of the hydraulic clutch 1li.
  • the clutch 14 then automatically couples the spur gear 11 with the cable drum 1i) so that the latter can take up the cable 23 in order to lift the load which is suspended on the cable.
  • the valve 27 is reversed in automatic response to rising pressure in the cond-uit 2S and admits uid into a supply conduit 28 and thence into a conduit 29 leading to the cylinder 3 of the pressure regulator 7.
  • the conduits 28, 29 communicate with each other through the rst control valve 6 whose adjusting element ta is preferably mounted on the control panel of the drivers cabin.
  • the setting of the valve 6 for lifting of loads is such that the conduit 3d is sealed,
  • the pressure in the chamber of the cylinder 8 rises subsequent to a rise in pressure in the working chamber of the clutch cylinder 24, whereby the uid entering the chamber of the cylinder 8 causes the piston rod 31 to adjust the pressure regulator 7 by moving in a direction to the right, as viewed in FIG.
  • the springs 32 also determine the initial pressure which prevails in the charnber of the cylinder 8 by biasing the piston which is connected to the rod 31 in a direction to the left, as viewed in FIG. 1. In other words, the selected bias of the springs 32 will determine the initial pressure of tiuid in the conduit 29.
  • the regulator 7 receives pressure fluid through a conduit 33 which is connected to a conduit 65 serving to convey fluid from the pressure side of the pump 19.
  • the conduit 65 is also connected with the pressure tank 21.
  • the regulator 7 will permit pressure fluid to flow at a controlled rate from the conduit 33 into a conduit 34 and thence into a feed conduit 35 discharging into the upper chamber of a doubleacting cylinder 36 for the brake band 13.
  • the cylinder 5a of the pedal 4 is connected with a conduit 39 leading to the conduit 26 and hence to the oil tank 18.
  • the pedal 4 cannot be depressed because the control valve 6 seals a discharge conduit 40 which is also connected with the cylinder 5a so that the pedal may be used as a rigid rest for the foot of the operator.
  • the drum 10 collects the cable 23 and thereby lifts the load as long as the control arrangement remains in the position of FIG. l, i.e., as long as the lever 1 continues to compress the return spring 2b in the chamber 2e of the upper signal transmitting cylinder 2 and as long as the control valve 6 continues to permit flow of fluid between the conduits 28, 29 but seals the adjoining ends of the conduits 30 and 40.
  • the person in charge simply rocks the lever 1 back to the neutral position shown in FIG. 1 so that the return spring 2b is free to expand and pushes the piston 2a in a direction to expose the discharge end of the supply conduit 26.
  • the pressure in the cylinder 8 of the pressure regulator 7 decreases so that the springs 32 can retract the piston rod 31 back to its starting position.
  • the regulator 7 then seals the conduit 33 from the conduit 34 so that the pressure in the brake cylinder 36 decreases whereby the spring 3S expands and applies the band 13 against the brake drum 12 to prevent further rotation of the cable drum 10.
  • the spring 38 preferably applies the brake band 13 before the lever 1 returns to the neutral position of FIG. l.
  • the pressure in the conduits 28, 29 and 25a drops still further and the clutch 14 is disengaged in response to contraction of its spring or springs 14a so that the spur gear 11 can rotate independently yof the cable drum 16.
  • the fluid which is expelled from the chamber of the cylinder 3 also enters a conduit 41 which discharges into the cylinder 43 of the second brake including the drum 16 and band 17.
  • Stich uid causes the band 17 to engage the periphery of the drum 16 so that the planetary transmission is coupled to the gear 11 via shaft 44 and controls the speed at which the drum 10 can pay out the cable 23.
  • One pinion 15g of the transmission 15 is shown in FIG. 2, and this pinion meshes with a sun wheel 15b which is rigid with the cable drum 10.
  • the band 17 allows the drum 16 to rotate with the sun wheel 15b.
  • the fluid which flows through the discharge conduit 42 automatically reverses the valve 27 so that the latter seals the discharge end of the conduit 25 and allows uid flowing from the conduit 42 to enter the conduit 28 and thence the conduit 29 and the cylinder 8 of the pressure regulator 7.
  • the latter again allows pressure fluid to ilow at a controlled rate from the conduit 33 to the conduits 34, 35 and into one member of the cylinder 36.
  • the coupling rods 37 are shifted against the bias of the spring 3S so that the band 13 is disengaged from the periphery of the brake drum 12 and the latter allows the cable drum 10 to rotate in a sense to lower the load which is suspended on the cable 23.
  • the lplanetary transmission 15 controls the speed at which the cab-le 23 is being paid out during lowering of the load. Such speed a-lso depends on the r.p.m. of the motor which drives the spur gear 11.
  • the motor is reversibile and can be operated at a plurality of speeds.
  • the band 17 is applied in a first step (i.e., immediately following movement of the lever 1 from its neutral position and in a clockwise direction, as viewed in FIG. l), and the fluid which'flows through the conduit 42 and valve 27 thereupon adjusts the pressure regulator 7 in the nextfollowing stage of operation.
  • the cylinders 2 and 3 may be replaced by suitable oil pressure regulators without in any way affecting the operation of the apparatus.
  • the pressure regulators will be connecte-d to the conduit 65 instead of receiving fluid directly from the oil tank 18. Return flow of oil will take place through the return conduits 64b and 64e so that the storing receptacle 49 (to be described in connection with FIG. 3) may be dispensed with.
  • the operator In order to convert the apparatus for operation which is controlled by the lever 1 and 'by the pedal 4 (while the spring 38 continues to be used as a means for mechanically applying t-he brake band 13 against the periphery of the bra-ke drum 12), the operator must actuate the adjusting element 6a of the control valve 6 in such a way that the valve 6 seals the conduits 28, 29 from each other and connects the conduit 30 with the conduit 40.
  • the cylinders 2 and 3 can send fluid only through the conduit 25a and on to the working chamber of the clutch cylinder 24 or to the conduit 41 and thence to the cylinder 43, depending upon whether the winch assembly is to lower or to lift the load.
  • the larger piston of the differential piston in the cylinder 5a sends pressure iluid through the conduits 40 and 30 and on to the cylinder 8 of the pressure regulator 7.
  • the latter admits pressure fluid a-t a controlled rate against the piston 3611 (see FIG. 4) in the cylinder 36 in order to compress the spring 38-and to disengage the band 13 from the brake drum 12.
  • the pressure which is determined by the regulator 7 is felt in the cylinder 36 and is also transmitted through the conduit 45 to act against the smaller piston of the differential piston in the cylinder Sa of the pedal 4.
  • the lower chamber of the brake cylinder 36 discharges fluid through a second feed conduit 46, through the control valve 9 and conduit 47, and back into the oil tank 18.
  • control valve 9 is adjusted by the element 9a in such a way that the conduit 34 communicates with the conduit 46 and that the conduit 35 communicates with the conduit 47.
  • the cylinder 8 causes the regulator 7 to admit pressure vad through the conduits 34 and 46 so that such fluid enters the lo-wer chamber of the cylinder 36 and the brake band 13 is applied directly by hydraulic pressure in a manner to be described in greater detail in connection with FIGS. 4 to 6.
  • the upper chamber of the cylinder 36 discharges fluid through the conduits 35, 47 and Iback into the tank 18.
  • the pressure which develops in the conduits 46 and 34 is felt in the conduit 45 and is applied against the smaller piston of the diterential piston in the cylinder a of the pedal 4 so that, by keeping his foot on the pedal, the operator feels that the pressure rises, i.e., that the brakes Iband 13 is being applied in response to the pressure of hydraulic fluid.
  • the conduits 25b and 35b respectively branch from the conduits 25a, 35 and are connected to a solenoid valve for end switching.
  • the conduits 64a to 64C are return conduits and the conduit 65 is a pressure line which connects to additional consumers of hydraulic pressure uid.
  • the signal transmitting cylinder 3 is connected with a conduit 48 leading to a storing receptacle 49 whose pressure and volumetric values are the same as those of the cylinder 43 for the brake band 17.
  • a cylinder 3 which is identical with the cylinder 3 of FIG. 1.
  • the person in charge must move the llever l-through the same distances and must overcome Athe same forces as in the embodiment of FIG. 1. Otherwise, the conversion of the control arrangement shown in FIG. 3 for various setups takes place in the same way as described in connection with FIG. l.
  • T he numeral 50 denotes in FIG. 1 a frame member which supports the winch.
  • the brake drums 12, 16 and the corresponding brake bands 13, 17 are shown in FIG. 1 one ⁇ below the other; actually, the two Ibra-ke drums are coaxial with the -ca'ble drum 1t) as clearly shown in FIG. 2.
  • the operating unit shown in FIGS. 4 to 6 is constructed and assembled in such a way that the control arrangement ofthe present invention can be readily converted for different operations without necessitating removal, replacement or substantial adjustments in the construction of the brake.
  • all that is necessary is to adjust the control valve 9 by means of the element 9a whereby the brake :band 13 can be applied against the 'brake drum 12 by spring pressure (spring 38) or by hydraulic pressure (when the iluid is admitted through the feed conduit 46 to enter the lower chamber of the cylinder 36).
  • the operating unit for the brake band 13 is shown in a position in which the band 13 may Ibe applied by the bias of the brake spring 38.
  • the band 13 comprises a fixed first end portion 13a and a movable second end portion 13b.
  • the xed end portion 13a is connected to a -bolt 51 which is mounted in an inverted U-shaped carrier ⁇ 52 having an upper :portion which straddles the cylinder 36.
  • the bolt 51 is further mounted in an inverted U-shaped yoke 53.
  • the movable second end portion 13b is reciprocable between the downwardly eX- tending legs of the yoke 53 and is attached to a bolt 54.
  • the latter is slidable in guide slots 53b provided in the legs of the yoke 53.
  • An elongated abutment rod 53a is ⁇ connected to the web at the upper end of the yoke 53 and extends toward the web 52a at the upper end of the carrier 52.
  • the rod 36e of the piston 36b in the cylinder 36 is supported by or coupled to the free end of the rod 53a.
  • the cylinder 36 receives pressure fluid through the feed conduit 35 so that the upper cylinder chamber 36d is under pressure.
  • the cylinder 36 then moves upwardly, as viewed in FIG. 4, Iby s-liding along the piston 36b, and lifts the bolt 54 through the intermediary of coupling rods 37 which are attached to a bottom end wall 36a of the cylinder 36.
  • the upper end of the piston rod 36C bears against the web 52a of the carrier 52 so that the piston 3617 remains stationary and the bolt 54 moves upwardly by sliding in the slots 5317.
  • the coupling rods 37 are disposed in the space enclosed -by the legs of the carrier 52.
  • connection between the lower end portions of the rods 37 and the bolt 54 comprises a bridge 37a.
  • a crosshead 37b which is rigid with the bridge 37a bears against the lowermost convolution of the spring 38 and causes this spring to store energy.
  • the upper convolution of the spring 38 bears against a second crosshead 55.
  • the distan-ce between the yoke 53 and the crosshead 55 may be varied by nuts 55a which mesh with the abutment rod 53:1.
  • the crosshead 55 is slidable along the coupling rods 37.
  • the upper cham-ber 36d of the cylinder 36 is connected with the tank 18 so that the uid can esca-pe via conduit 35 whereby the yspring 38 expands and moves the end portion 13b toward the lixed end portion 13a.
  • the spring 38 is compressed by admission of uid into the upper cylinder chamber 36d so that the cylinder 36 rises and the spring 38 is compressed while lthe end portion 13b of the ⁇ band 13 moves away from the xed end portion 13a.
  • the operator actuates the adjusting element 9a (see FIG. 1) of the control valve 9 to release a Bowden wire 58 which forms part of a locking device.
  • This locking device further comprises a locking member or bolt 57 ⁇ which is biased -by a spring 59 so that it enters the space between the crosshead 55 and bottom end wall 36a, see FIG. 6.
  • FIG. 1 shows that the Bowden wire is connected with the adjusting element 9a of the control valve 9 in such a way that the spring 59 is permitted to expand in automatic response to manipulation of the element 9a so that a single manipulation suces to set the operating means of FIGS. 4-5 for application of the band 13 by hydraulic pressure.
  • the adjusting element 9a is mounted in or on the control panel of the operators cabin.
  • the Bowden wire 58 is preferably released prior to actual adjustment of the Control valve 9 so that, as soon as the valve 9 admits compressed Huid into the feed conduit 46, the lower chamber of the cylinder 36 receives pressure fluid and the conduit 35 is then connected with the tank 18.
  • the cylinder 36 descends (because the piston 36b is fixed between the ⁇ abutment rod 53a and web 52a) and causes the -boltl 54 to move the end portion 13b toward the end portion 13a so that the band 13 is applied around the brake drum 12.
  • the transmission of motion to the bolt 54 takes places through the -bottom end wall 36a, coupling rods 37 and bridge 37a.
  • Such movement of the end portion 13b toward the end portion 13a results in tensioning of a return spring 60 which tends to maintain the band 13 in disengaged position -but is weaker than the brake spring 38.
  • the operator actuates the lever 1 in a manner as ⁇ described in connected with FIG. 1 so as to allow pressure fluid to escape from the lower chamber of the cylinder 36 whereby the return spring 60 contracts 'and moves the end portion 13b away from the end portion 13a. If the adjusting element 9a of the control valve 9 is then returned to the position of FIG. 1, the ⁇ wire 58 withdraws the locking bolt 57 against the bias of the spring 59 and the operating unit of FIG. 6 is ready to operate again in the manner as disclosed in connection with FIGS. 4 and 5, namely, the spring 38 is again free to apply the band 13 against the brake drum 12.
  • the cylinder 66 of FIG. 7 differentiates from the cylinder 36 of FIGS. 4 to 6 in that it comprises a centrally located partition 61 which is bounded by two spacer elements and is located between two fixed pistons 62.
  • the upper piston 62 is connected with a piston rod 62a which is secured to Vor -a-buts against the web 52a of the carrier 52.
  • the piston rod 62h of the lower piston 62 abuts against the rod 53a in the same way as shown in FIG. 4.
  • the feed conduits 35, 46 respectively communicate with cylinder cham-bers which are located at the opposite sides of the partition 61, and the upper end of the cylinder 66 is sealed against entry of foreign matter ⁇ by an ⁇ annular diaphragm 63.
  • the cylinder 66 need not be provided with an end wall such as the end wall 36a of the cylinder 36.
  • the conduit 35 admits pressure fluid into the chamber which is located at the underside of the partition 61, the cylinder 66 will descend and will cause the end portion 13b to move toward the end portion 13a so that the band 13 is applied against the periphery of the brake drum 12.
  • the .conduit 46 admits fluid into the cham-ber which is located at the upper side of the partition 61, the cylinder 66 will rise and will compress the spring 38. It is clear that the conduits 35, 46 communicate with the respective chambers during full stroke of the cylinder 66.
  • I provide a highly versatile machine which can be used as a crane or as an excavator, and wherein the conversion from one setup to another setup or vice versa can be carried out in a very simple and timesaving manner, i.e., by simply adjusting one or both control valves 6 and 9 whereby the locking or unlocking of the spring 38 takes place automatically by remote control (Bowden wire S) in response to manipulation of the adjusting element 9a for the control valve 9.
  • the wire 5S can conve-rt the operating unit for the brake 12, 13 from mechanical to hydraulic application of braking force or vice versa.
  • the improved control arrangement is equally useful in cranes wherein the winch comprises two or more cable drums. All that is needed in such multiplex Winches is to simultaneously block or release the springs in each of the operating units.
  • the initial bias of springs 32 for the regulator 7 may be selected in such a way that the regulator begins to regulate the pressure in dependency on uid pressure in the cylinder 24 or 43, and only when the clutch 14 or the braking device 15, 16, 17 is applied. Inversely, the clutch 14 or the braking device 15-17 can be disengaged only when the braking device 12, 13 is applied. Therefore, the load is under full control at all times, even during such intervals when the actuating lever 1 in or on the control panel is being shifted from neutral to an end position or vice versa.
  • the springs 32 of the pressure regulator 7 are adjusted with utmost precision to determine the exact moment when the device 7 begins to regulate the pressure in the hydraulic circuit. Such precision adjustment must be carried out only once and is necessary to determine theoverlapping of control functions.
  • the regulator 7 can control and vary the pressure gradually so that the braking device 12, 13 may be applied or disengaged with utmost accuracy and that the opposing moments are-relatively small, i.e., the takeover of load by the braking device will be effected smoothly.
  • the control arrangement of FIG. 3 exhibits the important advantage that, by actuating the le-ver 1, the operator in charge has the same feel as if the winch were controlled by a planetary brake.
  • the receptacle 49 causes the lever 1 to create in the hand which manipulates this lever the same sensation as if the cylinder -43 of the operating unit for the brake 15-17 were actually installed in the machine.
  • control valve 6 The function of the control valve 6 is to allow for a rapid conversion from the setup (a) to setup (b).
  • This control valve is mounted in the supply conduit 28 between the reversible valve 27 and the cylinder 8 of the pressure regulator 7 so that, in the setup (a), it connects the regulator with one of the cylinders 2, 3, depending on the direction (H or S) in which the lever 1 is moved from neutral position.
  • the cylinders 2, 3 are sealed from the cylinder 8 but the latter is connected with the cylinder 5a so that the pedal 4 may actuate the regulator 7 whereby the latter controls the braking device 12, 13 through the intermediary of the control valve 9.
  • the valve 6 seals the cylinders 2, 3 from the cylinder 5a so that the lever 1 then merely serves to control the clutch 14 and the braking device 15-17, depending upon whether the signal is transmitted by the cylinder 2 or 3.
  • the setup (a) all of the operations are controlled by the lever 1 and the pedal 4 serves as a foot rest whereas, in the setup (b), the operations are controlle-d by the lever 1 and by the pedal 4.
  • the differential piston 5 enables the operator to sense the pressure with which the brake 12, 13 is applied by the pedal 4.
  • This two-stage piston 5 can be replaced by two separate pistons of different diameters and a spring therebetween.
  • the larger-diameter piston of the differential piston serves to control the regulator 7 whereas the smaller-diameter piston controls the pressure in the conduit 45 and hence in the cylinder 36. Consequently, the fluid pressure acting upon the smaller-diameter piston is felt by the foot which rests on the pedal 4.
  • the cylinder 5a is preferably dimensioned in such a way that there is no volumetric change in the conduit 45 when the pedal 4 is depressed.
  • the reversing valve 27 insures that the stream of pressure fluid which applies the clutch 14 is not the same as the fluid stream which applies the braking device -17.
  • This valve 27 automatically seals the conduits 25, 25a from the conduits 41, 42 when the one or the other of the cylinders 2, 3 sends fluid through the supply conduit 28.
  • the valve 27 furthe-r insures that the same pressure regulator 7 can control the disengagement of the brake band 13 regardless of whether the load on the cable 23 is raised or lowered.
  • FIG. 8 there is shown a third hydraulic control arrangement which is shown in a condition ready to operate in accordance with the setup (a).
  • the control valves 6 and 9 are adjusted in such a way that a conduit 149 is sealed and that the feed conduit 46 communicates with the conduit 47 s o that the lower chamber of the cylinder 36 can discharge into the tank 18.
  • the pedal 4 is not in use. If the crane is to lift a load, the actuating lever 1 is rocked in the direction indicated by the larrow H. Instead of controlling two signal transmitting cylinders (such as the cylinders 2 and 3 of FIG. 1, the lever 1 of FIG. S controls alternatively two pressure regulators 102, 193.
  • the lever 1 operates the pressure regulator 102 whereby the latter connects the branch 165:1 of a pressure conduit 165 which branches from the conduit 65 with a return conduit 164 after the pressure uid has complete-d the work.
  • the conduit 165 receives pressure fluid and the conduit 164 treturns spent fluid into the tank 18.
  • the uid pressure which is necessary for regulating the lifting operation is transmitted through the conduits 25, 25a and directly to the cylinder 24 of the clutch 24.
  • the clutch 14 is applied and couples the driving element 11 of the prime mover with the cable drum 10, not shown in FIG. 8.
  • iluid pressure in the conduit 25 is communicated through the reversible valve 27, conduit 128, control valve 6, conduit 129, feed conduit 35, control valve 9 and on to the upper chamber of thejcylinder 36 so that the braking device 12, 13 is disengaged subsequent to application of the clutch 14 because the coupling rods 37 cause the movable end portion 13b of the brake band 13 to move away from the fixed end portion 13a against the bias of the spring 38.
  • the cable drum 11D begins to rotate and lifts the load which is attached to the cable 23.
  • the person in charge returns the lever 1 to the neutral position of FIG. 8 so that the pressure fluid can flow from the cylinders 24 and 36, through the corresponding conduits, through the pressure regulator 102 and through the conduit 164 vback to the tank 18.
  • the clutch 14 is then disengaged by the spring 14a and the brake band 13 is applied by the spring 38 whose bias is stronger than that of the spring 60.
  • the band 13 is applied before the lever 1 returns to its neutral position, and the band 13 is ⁇ also applied before the spring 14a is allowed to disenga ge the clutch 14.
  • the lever 1 For lowering of a load, the lever 1 is rocked in the direction indicated by the arrow S. This actuates the pressure regulator 103 whereby the pressure conduit 165 can communicate with the conduits 142 and 41 to admit pressure huid into the cylinder 43 of the operating unit for the braking device 15-17.
  • the band 17 is now applied against the brake drum 16.
  • the valve 27 is reversed in a fully automatic way so that the pressure uid can again flow through the conduits 128 and 129, control valves 6 and 9, and into the feed conduit 35.
  • the drum 16 is now braked and the planetary transmission is coupled with the gear 11 through the intermediary of the shaft 44.
  • the sun wheel of the planetary transmission is xed to the cable drum 10 so that the load descends at a speed determined by the r.p.m. of the prime mover which drives the gear 11. Such lowering takes place as soon as the pressure in the hydraulic circuit rises suiciently to eliect dis- 12 engagement of the 'brake band 13 subsequent to application of the brake band 17.
  • the coupling and braking moments are corelated in such a way that the load is controlled in each intermediate position including the neutral position of the lever 1, i.e., that the load cannot descend by gravity at the time the operator does not wish to start such descent.
  • control arrangement will constitute a combined pneumatic and hydraulic or purely a pneumatic arrangement.
  • a pressure reducing valve 70 (shown by broken lines) can be installed in the feed conduit 35 to change the exact moment when the control operations overlap.
  • the valve 70 may be replaced by a conventional braking force regulator.
  • the control arrangement of FIG. 8 constitutes a simplilication of the control arrangement which is shown in FIG. l.
  • the pressure regulators are connected with the source or sources (19 and/or 21) of pressure fluid in such a way that, in response to manipulation lof the actuating lever 1, the conduit 25a transmits pressure fluid directly into the cylinder 24 of the clutch 14 and that the conduit 41 transmits pressure fluid ⁇ directly into the cylinder 43 of the operating unit for the planetary braking device.
  • the cylinder 15a of the pedal 4 can send pressure fluid to the lower chamber of the cylinder 36.
  • the piston b of the pedal 4 is biased by a suitable spring 4a which normally holds it in starting position.
  • FIG. 8 does not require the pressure regulator 7 of FIG. 1 and/ or the receptacle 49 of FIG. 3. Also, the hydraulic circuit is much simpler because several of the conduits shown in FIG. 1 can be dispensed with. Furthermore, the cylinder 105a need not accommodate a differential piston but a simple piston 105! which is connected to the pedal 4. Still further, the force required to manipulate the lever 1 may be reduced to a minimum, namely, to such an extent that the operator must overcome only frictional forces.
  • FIGS. l and 2 Another difference between the control arrangements of FIGS. l and 2 resides in that, yfor the setup (a), the cylinder 36 of FIG. 8 receives pressure fluid directly from one of the pressure regulators 102, 103. In the setup (b) or (c), the cylinder 36 of FIG. 8 receives pressure fluid directly from the cylinder 105a of the pedal 4.
  • a winch comprising a cable drum
  • a braking device for said cable drum including a brake drum operatively connected with said cablefdrum, a brake band surrounding said brake drum and having a fixed end portion and a second end portion, and an operating unit for moving said second end portion toward and away from'said fixed end portion to thereby apply or disengage said band from said brake drum, said operating unit comprising a double-acting cylinder coupled to said second end portion, fixed piston means received in said cylinder, spring means for normally biasing said cylinder in a direction to apply said band, and releasable locking means for said spring means; and a fluid-operated control arrangement for regulating the operation of said unit including a circuit having a pair of feed conduits connected with said cylinder, a source of pressure fluid installed in said circuit, actuating means for selectively operating said locking means, and control means for selectively admitting pressure huid through said feed conduits so as to apply the band by the action of said spring means when said locking means is idle, to disengage said band when one of said feed conduits admits pressure fiui
  • control arrangement further comprises adjustable control valve means provided in said circuit and adjusting means operatively connected with said actuating means and with said control valve means for adjusting said valve means simultaneously with adjustment of said locking means.
  • said operating unit further comprises a U-shaped carrier coupled to the fixed end portion of said band and enclosing said cylinder, a yoke coupled to said fixed end portion and straddling the second end portion of said band, a rod assembly connected with said yoke, with said carrier and with said piston means and slidably supporting said cylinder, ⁇ a crosshead provided on said rod assembly, and coupling means connecting said cylinder with the second end portion of said band, said spring means being operative 'between said crosshead and said coupling means to urge said cylinder toward said yoke and to thereby bias said second end portion toward said fixed end portion.
  • said coupling means comp-rises a bridge connected to said second end portion, a second crosshead connected to said bridge, and a plurality of coupling rods connecting said second crosshead with said cylinder, said spring means constituting an expansion spring and being disposed between said crossheads.
  • said locking means comprises a bolt movable between said crosshead and said cylinder when the cylinder is moved in a direction to disengage the brake band, and resilient means for biasing said bolt to such position, said actuating means including remote control means for withdrawing the bolt against the bias of said resilient means.
  • said regulator begins to regulate the pressure in said circuit only when sai-d clutch or said second brake band is applied by means of an actuating member and via signal transmitting cylinder means in said circuit.
  • bias of said resilient means is variable by admission of press-ure fluid into said adjusting cylinder, preferably in dependency on the load carried by the cable of said cable drum.
  • control arrangement further comprises signal transmitting cylinder means, actuating means for said signal transmitting cylinder means, and a storing receptacle provided in sai-d circuit and connected with said signal transmitting cylinder means, the pressure and volumetric values of said receptacle corresponding to those of a cylinder in a planetary brake.
  • control arrangement further comprises a pair of signal transmitting cylinders, an actuating member for operating one of said signal transmitting cylinders at a time to thereby initiate lifting or lowering of loads suspended on the cable of said cable duim, a reversible valve, discharge conduits connecting said signal transmitting cylinders with said reversible valve and further conduits connected with said discharge conduits, said reversible valve being arranged to respectively seal said further conduits and said discharge conduits from each other.
  • said circuit further comprises a supply conduit connected with said reversible valve to deliver liuid in response to actuation of either one of said signal transmitting cylinders, a first adjustable control valve connected in said supply conduit, a pressure regulator ⁇ between said control val-ve and the cylinder of said operating unit, a further cylinder having a piston provided with a pedal, conduit means connecting said further cylinder with said control valve and with said feed conduits and a second adjustable control valve connected between said further cylinder and said feed conduits, said first control valve being adjustable to a first position to thereby seal said signal transmitting cylinders from said pressure regulator.
  • control means comprises a pair of pressure regulators connected with said source of pressure fluid, a third conduit directly connecting said pressure regulators with the cylinder of said clutch, a fourth conduit connecting said pressure regulators with said feed conduits, control valve means and a reversible val-ve .provided in said fourth cond-uit, a fifth conduit connecting said pressure regulators with the cylinder of said second operating unit, and actuating means for selectively operating one of said pressure regulators at a time.
  • control means also comprises a further cylinder having 3,300,190 15 16 a spring-biased piston provided with a pedal, a sixth con- References Cited by the Examiner duit connecting said further cylinder with a tank provided UNITED STATES PATENTS in said circuit, and a seventh conduit connecting said further cylinder with said control valve means in such 2,427,471 9/1947 O'Sgood 254"185 a Way that said control valve means can seal said Vfourth 5 2'9471397 8/1960 Pletsch, 254-'185 conduit and then connects said seventh' conduit with 312441404 4/1966 Bender 25'4-185 one of said feed conduits.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Braking Arrangements (AREA)
  • Mechanical Control Devices (AREA)
US508195A 1964-11-17 1965-11-17 Control arrangement Expired - Lifetime US3300190A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DER0039269 1964-11-17

Publications (1)

Publication Number Publication Date
US3300190A true US3300190A (en) 1967-01-24

Family

ID=7405738

Family Applications (1)

Application Number Title Priority Date Filing Date
US508195A Expired - Lifetime US3300190A (en) 1964-11-17 1965-11-17 Control arrangement

Country Status (4)

Country Link
US (1) US3300190A (de)
AT (1) AT260469B (de)
CH (1) CH452150A (de)
GB (1) GB1082010A (de)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4093034A (en) * 1975-12-15 1978-06-06 Caterpillar Tractor Co. Vehicle supported winch
US4337926A (en) * 1980-09-02 1982-07-06 Eaton Corporation Winch control
US20080260318A1 (en) * 2007-04-18 2008-10-23 Schaeffler Kg Roller bearing with a braking device

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3756564A (en) * 1970-10-05 1973-09-04 Gearmatic Co Ltd Power control winch
CN103588135A (zh) * 2013-11-13 2014-02-19 安徽省宿州市龙华机械制造有限公司 一种用于矿用绞车的断电急停装置

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2427471A (en) * 1942-01-12 1947-09-16 Joy Mfg Co Hoist control means
US2947397A (en) * 1958-07-23 1960-08-02 Bucyrus Erie Co Fluid clutch control for clamshell excavators
US3244404A (en) * 1962-10-22 1966-04-05 Emil A Bender Drawworks assembly

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2427471A (en) * 1942-01-12 1947-09-16 Joy Mfg Co Hoist control means
US2947397A (en) * 1958-07-23 1960-08-02 Bucyrus Erie Co Fluid clutch control for clamshell excavators
US3244404A (en) * 1962-10-22 1966-04-05 Emil A Bender Drawworks assembly

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4093034A (en) * 1975-12-15 1978-06-06 Caterpillar Tractor Co. Vehicle supported winch
US4337926A (en) * 1980-09-02 1982-07-06 Eaton Corporation Winch control
US20080260318A1 (en) * 2007-04-18 2008-10-23 Schaeffler Kg Roller bearing with a braking device

Also Published As

Publication number Publication date
AT260469B (de) 1968-03-11
GB1082010A (en) 1967-09-06
CH452150A (de) 1968-05-31

Similar Documents

Publication Publication Date Title
US1960996A (en) Hydraulic braking apparatus
GB1004913A (en) Hydraulic winch control mechanism
US2279597A (en) Controlling means for hoists and winches
US3300190A (en) Control arrangement
US3859791A (en) Fluid operated hydraulically lapped control apparatus
US3785503A (en) Boom control mechanism for tractors or the like
US4398698A (en) Freefall winch system and method of operation
US2990925A (en) Transmission clutch control
US3128861A (en) trondsen
US4337926A (en) Winch control
US3371543A (en) Engine power takeoff drive
US4136855A (en) Hoist drum drive control
US2749767A (en) Power transmission
US3198027A (en) Hydraulic transmission control
US1932685A (en) Brake appplying means
US2945572A (en) Hydraulic control of brakes
US3651905A (en) Clutch and brake controls for clamshell hoist
US3683618A (en) Friction clutch or brake system
US2021580A (en) Hoisting mechanism
US3347044A (en) Dual engine controls
US2168654A (en) Brake operating mechanism
US3203187A (en) Dual-cylinder hydraulic actuator for automotive clutch and brake control
US3268211A (en) Control system for winches and the like
US3039576A (en) Fluid system for a windlass
US3939950A (en) Fluid operated brakes and reversing clutches for winch drums