US3746115A - Hydraulic control apparatus for a hydraulic machine - Google Patents

Hydraulic control apparatus for a hydraulic machine Download PDF

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US3746115A
US3746115A US00216187A US3746115DA US3746115A US 3746115 A US3746115 A US 3746115A US 00216187 A US00216187 A US 00216187A US 3746115D A US3746115D A US 3746115DA US 3746115 A US3746115 A US 3746115A
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limiting
control apparatus
limiting unit
piston
pressure
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US00216187A
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P Bosch
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Robert Bosch GmbH
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Robert Bosch GmbH
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/38—Control of exclusively fluid gearing
    • F16H61/40—Control of exclusively fluid gearing hydrostatic
    • F16H61/46—Automatic regulation in accordance with output requirements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/08—Regulating by delivery pressure

Definitions

  • a control apparatus for an adjustable hydraulic machine includes a power amplifier for adjusting the hy- [30] Foreign Application Priority Data draulic machine under the control of a control valve Jan. 15, 1971 Germany P 21 01 730.1 generally Set y manual Setting meahs- Limiting "hits are selectively and dctachably attached to supporting 521 US. Cl. 180/66 R, 180/77 R, 60/19, means, and respond to excessive fluid Pressure, flow, or 60/443, 44 60/45 1 60/452 torque, to influence a limiting valve which controls the 511 1m.
  • the present invention relates to a hydraulic control and regulating apparatus for a hydraulic machine, which may be a pump or hydraulic motor, which has a pressure responsive power amplifier whose position is controlled by a control valve so that the power amplifier sets the adjusting means of the hydraulic machine, following the position set by manually operated setting means.
  • German Pat. 1,528,382 discloses a control apparatus of this type which is provided with a lever on which the force of a biassing spring and of a control piston act in response to the pressure in the hydraulic system, and which determines the position of the piston of a power amplifier which adjusts the stroke of the hydraulic machine, such as an axial piston pump.
  • the apparats of the prior art is capable of obtaining the follow-up control, a regulation of the torque, and a limiting of the pressure of the machine.
  • the apparatus has the disadvantage that only a single control or regulating operation can be carried out in a particular position of the biassing means.
  • the present invention provides limiting units which can be selectively mounted on supporting means of the hydraulic machine or control apparatus, and which respectively controls a limiting valve, irrespective of whether one or several limiting units are used.
  • the limiting valve influences the control valve to operate the power amplifier to correct the position of the adjusting means of the hydraulic machine to reduce the flow volume for reducing the excessive flow conditions to which one or several limiting units have responded.
  • the setting means include a manually operated member connected with the valve slide of the control valve for adjusting the position of the same when a follow-up control by the power amplifier is being carried out.
  • the arrangement of the invention permits it to use one or several limiting units, singly or in combination, in accordance with the flow condition or conditions which are to be corrected. It is advantageous to construct the limiting units with bodies having threads for being threaded into threaded bores of attaching portions of the supporting means. For example, three attaching portions with threaded bores may be provided, and limiting units for limiting flow pressure, flow volume or amount, and torque can be threaded into the threaded bores, if desired, but it is also possible to use any one of the limitingunits alone, or different combinations of two limiting units, which can be easily exchanged and replaced, which is advantageous also for repairs.
  • the pressure and torque limiting units can operate with the fluid pumped in forward or reverse direction, but these limiting units are also fully effective when the hydraulic machine is used as a hydraulic motor.
  • the flow amount limiting unit is only operative in one flow direction, which has been found sufficient for practical use.
  • FIG. 1 is partly a sectional view, and partly a schematic diagram illustrating a control apparatus according to the present invention applied to a hydrostatic transmission including a pump and a hydraulic motor driving wheels of a car supporting the hydrostatic trans mission and a combustion engine driving the pump of the transmission, the control apparatus being shown with a pressure limiting unit and with a flow limiting unit;
  • FIG. 2 is partly a sectional view, and partly a schematic view, illustrating another part of the apparatus shown in FIG. 1 comprising a torque limiting unit;
  • FIG. 3 is a schematic view illustrating a torque limiting unit controlled from a brake pedal and a gas pedal of a combustion engine driving the hydraulic machine;
  • FIG. 4 is a fragmentary elevation illustrating a modified part of the apparatus shown in FIG. 2;
  • FIG. 5a is an elevation
  • FIG. 5b is a front view taken on line b, b in FIG. 5a, and being a front view, partly in section of the device shown in FIG. 5a;
  • FIG. 6 is a schematic view illustrating another modification of the apparatus shown in FIG. 2.
  • a housing 11, only partly shown in FIG. 1, has two parallel stepped bores 12, 13, partly provided with thread, in which a pressure limiting unit 14 and a flow limiting unit 15 are located.
  • the pressure limiting unit 14 includes a cartridge body which is tightly threaded into the stepped bore 12, and has a stepped blind bore 17 in whose lower portion 17', a measuring piston 18 is tightly guided.
  • Piston 18 has a central flange 19 on which the lower end of a spring 20 abuts whose upper end abuts a shoulder formed by the bore 11a in supporting means 12.
  • Meausring piston 18 includes a pressure pin 21 which in the position of rest of the pressure limiting unit 14 projects through bore 11a. In this position, flange I9 abuts shoulder 22 formed by the bore portions 17' and 17''.
  • the spring 20 can be pretensioned by threading the body I6 more or less deeply into the stepped bore 12.
  • the flow limiting unit 15 includes a cartridge body 24 tightly screwed into the stepped bore 13, and having a stepped bore 25 in which a stepped measuring piston 26 is slidingly guided.
  • a piston portion 27 divides a space 28 into a lower pressure chamber 28 and an upper pressure chamber .28" which is bounded by a fixed partitioning plate 29 on which the flange 30of the stepped piston 26 abuts in a position of rest due to the action of a spring 31 abutting flange 30 and having an upper end supported on an annular shoulder formed in supporting means 12 by the bore 11b.
  • a pressure pin portion 32 of the stepped piston 26 projects through opening 1 1b.
  • a channel 33 connects pressure chamber 28" with a connector bore 34 in body 24 to which a pipe can be attached, as schematically indicated by the line 89.
  • the force of spring 31 can be adjusted by screwing the body 24 more or less deeply into the stepped bore 13.
  • Body 16 is provided on the outer surface with an annular groove 35 and 36, respectively, with which a channel 37 in the supporting means 12 communicates.
  • Channel 37 is continued by flow line 91, as schematically shown.
  • the height of each annular groove 35, 36 is substantially greater than the diameter of the channel 37.
  • a transmitting plate 38 is located, as schematically illustrated in a perspective view in FIG. 1.
  • the rectangular plate 38 has lateral portions projecting beyond the bore portions 11a and 11b of the stepped bores 17, 26 and has marginal fulcrum bulges 39 and 39', respectively, which rest on the top face of the supporting means 11, permitting tilting of plate 38.
  • a limiting valve 40 is located above the tiltable plate 38, and has a slide 42 which is guided in a blind cylinder bore 43 of a portion of the supporting means 11.
  • Slide 42 has two axially spaced annular grooves 45, 46 which are separated by a piston portion 44.
  • the cylin der bore 43 has an annular groove 47 into which a conduit 48 opens.
  • a conduit 49 opens in the cylinder bore 43 above the piston portion 44, and another line 50 opens below piston portion 44.
  • Tiltable plate 38 has an axially projecting pin 51 at one lateral end.
  • Conduit S is connected by branch conduit 52 with an adjustable and reversible pump 53, for example an axial piston pump, whose adjusting means 54 can be operated by meansof a power amplifier 55 which includes a differential piston 57 having a larger piston portion 57, dividing the cylinder 56 into two chambers 58 and59, and a smaller piston portion 57" which projects out of cylinder 56.
  • Piston portion 57" is mechanically connected by a link 60 with the adjusting means 54 of the pump 53.
  • the adjusting means 54 is a double-armed lever cooperating with two pistons located in two cylinder bores of a part of pump 53.
  • Pump 53 and the adjusting means 54 are also shown in a schematic illustration on the right side of FIG. 1 where pump 53 is shown to be driven by a prime mover which may be a combustion engine A.
  • Conduit 49 is also connected with pump 53 by branch conduit 61.
  • the two branch conduits 52 and 61 are connected by conduits 62 and 63, respectively, with a reversing valve 64 which includes a reversing piston 65 which is shil'table between two end positions for connecting branch conduits 62, 63, respectively, with a conduit 66 which opens into a conduit 67.
  • One end of conduit 67 opens into the pressure chamber 59 of cylinder 56 of the power amplifier 55, while the other end of conduit 67 communicates with a port 730 in the housing or valve body 68 of a control valve means 69.
  • Valve body 68 has a longitudinal cylinder bore 70 in which a control slide 71 is slidingly guided.
  • Control slide 71 has two annular grooves 72, 73 separated by a piston flange 74 whose axial width is slightly greater than the diameter of a bore or port 75 in valve body 68.
  • a schematically shown conduit 76 opens into port 75,
  • the cylinder bore 70 of control valve 69 has two annular shoulders 77, 78 which are spaced a distance equal to the axial length of control slide 71.
  • Each shoulder 77, 78 is engaged by a disk 79 and 80, respectively, on which springs 81 and 82 abut which are supported by the end walls of the valve body 68.
  • springs 81 and 82 center control slide 71 by means of disks 79, 80.
  • Each disk 71 has a central bore 79, 80.
  • a conduit 48, with a throttle 84, connects the chamber in which spring 81 is located with the annular groove 47 in the limiting valve 40.
  • conduit 67 which extends to the chamber 59 of the power amplifier 55, opens into a port 73a in valve body 68 located on the right side of piston flange 74 when control slide 71 is in the illustrated position of rest determined by springs 81 and 82.
  • a port 86' On the left of flange piston 74, a port 86' is located, which is connected with a discharge reservoir 86.
  • the space 87 in the valve body 68 is connected by a conduit 88 with one end of the cylinder of the reversing valve 64.
  • Conduit 49 is connected by conduit 89 with the connector bore 34 in the cartridge body 24 of the flow lim iting unit 15.
  • a throttle 90 is provided in conduit 49 between the connecting point of conduits 89, 49, and the connecting point of conduits 61, 49.
  • Conduit 67 is connected by a conduit 91 with channel 37 in supporting housing means 11.
  • Conrol slide 71 carries a fixedly secured pivot means which projects out of a slot 93 in valve body 68 of control valve 69.
  • a connecting link 94 is pivotally connected with pivot means 92 at one end, and with a double armed lever 95 at the other end. The free end of lever 95 is articulated to link 60 which connects power amplifier piston 57 with the adjusting means 94 of pump 93.
  • a resilient linkage 98 is articulated, which is connected with a manually operated setting lever 97.
  • the resilient linkage 96 includes two cranked rods 98, 99 which are yieldingly connected by a spring 100.
  • Setting lever 97 is mounted for angular movement in a bearing 101 which is supported by stationary supporting means.
  • a conduit 50 connects the limiting valve 40 with a hydraulic motor 102 which drives wheel means 103.
  • Conduit 49 also connects limiting valve 40 with the hydraulic motor 102, but is shown partly broken off for the sake of clarity of the illustration.
  • pump 53 and hydraulic motor 102 together constitute a hydrostatic transmission with a closed fluid circuit by which the wheels 103 of a vehicle are driven.
  • the delivered fluid volume of pump 53, and thereby the speed of the wheels 103 and of the vehicle, is set by setting lever 97. If the piston 42 of the limiting valve 40 is in the illustrated lower position, the two spaces 83 and 87 of the control valve 69 are connected by conduits 48, 49, 61, 62 and 88. Consequently, no one sided pressure acts on control slide 71 which can be shifted by means of setting lever 97, and linkage means 94, 95, 92 to any desired position for controlling the flow into and out of the pressure chamber 58 of the power amplifier 55 which operates the adjusting means 54 of pump 53 for adjusting the delivered fluid volume and direction of flow of fluid in pump53.
  • the flow of pressure fluid for controlling the differential piston 57 of the power amplifier 55 is as follows:
  • control slide 71 If control slide 71 is shifted to the right against the action of spring 82, pressure fluid from pressure chamber 58 of the power amplifier'55 flows through conduit 76 and annular groove 72 to the reservoir 86.
  • the pressure in pressure chamber 59 shifts the differential piston 57 also to the right as viewed in FIG. 1, so that'the delivered fluid volume of the pump 53 is increased so that the vehicle moves fast or slow depending on the angular displacement of setting lever 97.
  • conduit 50 becomes the high pressure conduit
  • reversing valve 64 connects branch conduit 63 with conduit 66.
  • the operations of the control valve 69, power amplifier 55, and adjusting means 54 take place as described above, but the wheels 103 turn rearward, and the direction of movement of the vehicle is reversed.
  • measuring piston 18 is moved upward against theaction of spring 20.
  • the pressure required for the displacement of the measuring piston '18 is supplied from pump 53 to the pressure limiting unit 14 through conduit 62, reversing valve 64, conduits 66,67,91, conduit 37 in supporting means 11, and annular groove 35 into the end portion 17 of the stepped bore 17.
  • Pressure pin 21 of measuring piston 18 raises the left end of the tiltable plate 38 which turns about the marginal 'fulcrum bulge 39' in clockwise direction, so that the limiting piston 42 of the limiting valve 40 is raised against the action of spring 41 so that piston portion 44 of limiting piston 42 interrupts the connection between conduit 48 and conduit 49, and then connects, during further upward movement, the high pressure conduit 48 with the low pressure conduit 50 so that pressure fluid flows out of chamber 83 of control valve 69 to the low pressure side of the pump.
  • the high pressure prevailing in chamber 87 of control valve .69 displaces control slide 71 against the action of spring 81 to the left, as viewed in FIG. 1, so that conduits 67 and 76 are connected by the annular groove 73 on the control slide 71. Pressure fluid can now flow, as described above,
  • limiting piston 42 assumesagain the illustrated position in which the spaces 82,83 in the control valve 69 are connected with each other so :that thedifferential piston 57 of the power amplifier '55returns to theposition'corresponding to the previously manually selected position of setting lever97.
  • the hydrostatic transmission '53, 102 is used for driving'a vehicle,.and in the event that the same moves downward on a slope due to the action'of gravity, hydraulic motor 102 is operated as a;pump, and pump 53 isoperated as a hydraulic motor. -If in this operational conditiomthe pressure of the'fluid rises above the maximum limitto'whieh the pressure limiting unit 14 is set, pump53 is adjusted to a-greater delivery of fluid so that the transmission ratio of :the hydrostatic transmission is reduced. In thismanner, the pressure limiting unit 14 is effective under all operating conditions.
  • flow limiting unit 15 becomes effective to reduce 'the'pumped volume.
  • the function ofthe flow limiting unit 15 is as follows: a
  • Throttle 90 produces a pressure differential and the pressure upstream of throttle 90, in conduit-61 acts in pressure chamber 28' of the cartridge body 16, since it is transmitted through branch conduit 62, reversing valve64, conduit 66, 67,
  • the lower pressure'downstream of throttle 90 is effective in pressure chamber 28" and is transmitted by the fluid in conduit 89 and channel 33.
  • the opposite effective faces of the Stepped limiting piston 26 are of equal size.
  • the setting lever 97 remains in its previously set position when the differential piston 57 of power amplifier 55 acts on the adjusting means 54, since the resilient linkage 96 yields without displacing setting lever 97.
  • the maximum limit of the pumped flow can be varied by screwing the cartridge body 24 of the flow limiting unit more or less deeply into the threaded portion of the stepped bore 13, which varies the pretension of spring 31.
  • the above-described hydraulic control circuit can be provided with a torque regulating and limiting unit 106 in addition to any one of the limiting units 14 and 15, but it is also possible to use only the torque limiting unit 106, and to omit the units 14 and 15. In the following description a preferred embodiment is described in which the torque limiting unit 106 is used in addition to the pressure limiting unit 14 and to the flow limiting unit 15.
  • a third stepped bore 105 is .provided, which has a threaded portion 105a into which a cartridge body 107 is tightly screwed.
  • a measuring piston 108 is slidingly mounted in a stepped bore 109 in the cartridge body 107.
  • the measuring piston 108 has a central flange 110 and projects the illustrated position of rest, with a pressure pin 112 through an opening forming the narrowest portion of the stepped bore 105. In this position, the flange 110 abuts an annular shoulder 113 of the stepped bore 105, as shown in FIG. 2.
  • the pressure pin 112 is in contact with a doublearmed lever l 14 which has a turning axis M, and is provided with lateral curved bulges 115, 116 which are equidistant from the turning axis M.
  • the turning axis M of the lever I14 can be shifted by means of a linkage 117, 118 which is guided in a guide means 119 for straight movement.
  • the movement of the turning axis M by means of the linkage takes always place in adirection perpendicular to the direction of movement of the measuring piston 108.
  • Lever l 14 is displaced by the linkage I17, 1 19 by the differential'piston 57 of power amplifier 55 which is connected by a linkage 120 and a connecting member 121 with linkage rod 117.
  • connecting member 121 can also be varied by a shifting rod 112 guided in guide means 123 for rectilinear movement.
  • the movement of the connecting member 121 is preferably perpendicular to the movement of the differential piston 57.
  • the transmission ratio of the linkage means 117, 118, 121 is varied.
  • the above described arrangement effects an adjustment of the axis M of lever 114 proportional to the fluid volume delivered by pump 53. If the delivered fluid volume is zero, the axis M of lever 114 intersects with the axis of measuring piston 108 in a point.
  • the bulges 115, 116 of lever 114 support a onearmed lever plate 124 which is mounted for turning movement about a shaft 125 mounted in bearing portions 126, 127 whose position can be slightly adjusted so that lever arm plate 124 is slightly slanted with hear ing 126 acting as a fulcrum.
  • the projecting pin 51 of tiltable plate 38 rests on the lever plate 124 on the outer end remote from shaft 125.
  • a circular track 128 is provided on which rests a roller 129 mounted on a piston 131 which is biassed by a spring and slidingly guided in a lever 132 which has a journal 133 mounted for angular movement in a stationary bearing 134.
  • the radius of the curved track 128 corresponds to the distance of the curved track 128 from the axis of bearing 134.
  • Lever 132 has an arm 135 which is either set to a particular angular position which may, for example, correspond to the maximal permissible torque of the combustion engine A, or which is connected with the gas pedal and linkage of the vehicle in such a manner that every rotary speed of thecombustion engine A obtained by the driver by operation of the gas pedal, not shown, is associated with a specific drive torque of pump 53, note FIG. 3. In the latter case, the direction of travel of the vehicle is preselected by turning the setting lever 97 to the end position, whereupon the vehicle is operated by simultaneously selecting the rotary speed of the combustion engine A, and the torque of pump 103 by means of the gas pedal.
  • the axis or turning point of lever 114 from the axis of the measuring piston 108 is designated a, and the constant distance of the axis M from bulge 115 is designated b,.
  • the respective lever arms correspond to a particular position of the differential piston 57 of the power amplifier 55.
  • the force P of spring 130, andthe turning moment acting on the lever plate 124 is independent of the position of the turning point or axis M of lever 114, as far as magnitude is concerned.
  • the counter moment results from the force acting on measuring piston 108 multiplied by the length of lever arm a and is proportional to the fluid volume delivered by pump 53.
  • the force acting on measuring piston 108 is a product of the surface fm of the measuring piston 108 on which pressure acts, multiplied by the fluid pump pressure p.
  • the required condition for a regulation of the torque is pressure of the delivered fluid p multiplied by the volume of the delivered fluid is constant. This condition is obtained in the present case if p fm.a P,-,.b, wherein P constitutes the force of spring reduced to the engaging points of bulges 115 or 116 between lever plate 124 and lever 114.
  • the pressure p of the transported fluid is supplied to the measuring piston 108 through a channel 37, as described with reference to FIG. 1. If during rising of the fluid pressure, the turning moment t.fm.a exceeds the turning moment P b lever 114 is turned in clockwise direction as viewed in FIG. 2. Bulge 115 engages and raises the lever plate 124 which raises the right end of tiltable plate 38 by engaging projecting pin 51. The tilted plate 38 displaces the limiting piston 42 of the limit valve 40 in upward direction, whereupon the differential piston 57 of the power amplifier 55 operates the adjusting means 54 of pump 53 to move toward the left for obtaining a shorter piston stroke, as explained above in the description of the operation of the pressure limiting unit 14.
  • Pump 53 may be an axial piston pump with a swash plate on which the piston shoes slide, and whose angular position is varied by the adjusting means 54 upon displacement of differential piston 57, the lever arm a being shortened due to the operation of the linkage 117, 118, 121, 120.
  • lever plate 124 is angularly displaced in clockwise direction, and the limiting piston 42 of the limiting valve 40 is returned to its initial position of rest by angular displacement of lever plate 124 and of tiltable plate 38.
  • the limit of the maximal torque can be adjusted by turning lever 132 so that the turning moment of the force of spring 130 on the axis of lever plate 124 is varied between zero and maximum.
  • the curvature of the curved track 128 is selected so that upon turning of lever 132, the pretension of spring 130 is not changed, or only slightly changed.
  • the curvature of the curved track is substantially in accordance with a segment of a circle whose radius corresponds to the distance of the curved track 128 from the axis of journal 133 and bearing 134.
  • the turning moment acting on the lever plate 124 is zero when the force acting on roller 129 is directed through the axis of lever plate 124 defined by bearings 126, 127 and journals 125. This turning moment rises as lever 132 is turned a greater angle which means that the point where the force of spring 130 acts, is displaceable along the lever plate 124.
  • lever 114 acts through bulge 116 on the lever plate 124 upon starting of the limiting of the torque, due to the fact that the turning'point or axis M is now located on the left of the axis of the measuring piston 108, as viewed in FIG. 2.
  • the function of the torque limiting unit 106 is not changed in any manner.
  • pump 53 is set to a smaller volume of delivered fluid.
  • a gas pedal 135 is turnable about a stationary bearing 136, and has an arm 137 on which a spring 137a acts to move gas pedal 135 to a normal position abutting a stop.
  • Two rods 138, 139 are articulated to arm 137.
  • Rod 139 is connected with the regulator 140a of the injection pump 140 of the combustion engine A, while the rod 138 carries a guide 141 with a slot 142 in which a rod 143 is located.
  • Rod 143 also passes through a slot 144 in a guide member 145 which is connected by a link 146 with an arm of a double-armed brake pedal 148 which is mounted for turning movement in a stationary bearing 149, and is urged by a spring 148a to a normal position abutting a stop.
  • a resilient connector forms part of the link 146, which also carries an abutment 146' cooperating with an adjustable stop 150.
  • the vehicle is provided with a conventional friction brake 151 which has a brake cylinder 15] connected by a conduit 152 with a master brake cylinder 153.
  • Master brake cylinder 153 includes a spring loaded contact pin 154.
  • the drive power is selected as usual by depression of the gas pedal which acts through rod 139 on the regulating means a of the injection pump 140, and also acts through rod 138 with guide 141 and slot 142, on rod 143 and on lever 132, described in detail with reference to FIG. 2. If the vehicle is to be braked, the driver releases the gas pedal 135 so that a spring 132" retracts lever 132 to the illustrated position in which the pump torque is zero. The force of spring 130 extends along a line through the bearing 127 of the lever plate 124. The vehicle rolls without being driven or braked.
  • the pressure in the hydrostatic transmission 53, 102 drops substantially to the pressure of the low pressure side of the pump.
  • the rod 146 sets lever 132 to a torque which is greater than zero.
  • the at first small drag pressure in the hydrostatic transmission 53, 102 rises, and the vehicle speed is reduced.
  • the selected and set maximum torque is equal to the A maximum permissible drag torque of the combustion engine A. If even stronger braking is required, further depression of the brake pedal 148 results in engagement of the actuator pin 154 of the piston of the master brake cylinder 153 so that the friction brake 151 is operat ed. To permit such further angular displacement of the brake pedal 148, linkage 146 is provided with the resilient connector means 147.
  • FIG. 4 illustrates a modifiction of lever 114 which was described with reference to FIG. 2.
  • a bar 156 carries two spaced rollers 157, 158, which corresponds to the bulges l 15, 1160f lever 114, and are in contact with the lever plate 124 so that the friction of the mechanism is reduced.
  • the torque limiting arrangement described with reference to FIG. 2, can be simplified as shown in FIGS. 5a and 5b.
  • the straight guiding means 123 of connecting member 121 is replaced in the embodiment of FIGS. 5a, 5b by a stationary straight guide 159 engaged by a lever 160, which replaces lever 114.
  • Lever 160 includes a bar 161 with a central bulge 162 which abuts the straight guide means 159.
  • Bar 161 carries two pairs of rollers 164 to 167 on opposite sides which engage the lever plate 124 into whose slot 163 the straight guide means 159 projects.
  • the rollers 164 to 167 are in rolling engagement with the bottom face of lever plate 124.
  • variable load on lever plate 124 can be obtained by hydraulic means, instead of by spring 130.
  • the lever plate 124 is supported with journals 125 in stationary bearings for angular movement.
  • a hydraulic cylinder and piston motor 168 acts to which fluid is supplied by an auxiliary pump 170.
  • the pressure exerted by the cylinder and piston means 168 is determined by a settable pressure limiting valve 169 which discharges if the pressure in the cylinder and piston means 168 rises above a maximum.
  • the torque limiting unit 106 is replaced by a flow limiting unit 15 of the type described with reference to FIG. 1, the straight guide means 119 of the rod 118 is removed.
  • lever plate 124 is turned about the bearins 126, 127 to a slanted position, a remote control of the differential piston 57 of the power amplifier 55 is possible.
  • the pressure chamber 28" of the flow limiting unit 15 is releived, and the lower pressure chamber 28' is supplied with fluid from a channel 179 in the cartridge body 24 which must be connected with the conduit containing pressure fluid. Channel 37 must be closed.
  • a particular position of the differential piston 57 of the power amplifier 55 is correlated in which positions a reduced force P of spring 130, see FIG. 3, and the pressure force acting on the stepped piston 26 of the flow limiting unit 15 are in equilibrium. if the control pressure is sufficient, the
  • remote control can be used for pump 53 pumping the fluid in forward and reverse directions.
  • the several described limiting units become regulators if the control slide 71 of the control valve 69 is not centered bysprings 81, 82 acting on the ends of control slide 71, but is pretensioned in only one direction by spring 96, or by springs 171, 172 shown in FIG. 1 to act in opposite directions on the setting lever 97'.
  • conduits have been shown as single lines, but it will be understood that such conduits may be pipes, or channels or ducts in the supporting housing means 11.
  • One or several limiting units can be combined in an apparatus according to the present invention, depending on the desired control or regulating function.
  • pump 53 an adjustable hydraulic motor can also be controlled or regulated.
  • the pressure and torque regulations is effective during operation of a hydraulic machine as pump or motor operating for pumping the fluid in forward or reverse directions so that four operating conditions are possible.
  • Hydraulic control apparatus for a hydraulic machine having adjusting means for regulating the quantity of fluid transported by said hydraulic machine, comprising in combination, pressure responsive power amplifier means for operating said adjusting means, and having power chamber means, control valve means including a movable valve slide forming pressure chamber means communicating with said power chamber means; manually operated setting means connected with said valve slide for setting said valve slide to different control positions for actuating said power amplifier means to operate said adjusting means so that the hydraulic machine is adjusted in accordance with the selected position of said setting means; supporting means having a plurality of attaching portions; a plurality of limiting units for limiting different flow conditions, and
  • each limiting unit having a position of rest and an operative position, and moving to said operative position when an undesirable flow condition occurs, at least one of said limiting units being detachably and exchangably mounted in a selected one of said attaching positions; a transmitting device mounted on said supporting housing in the region of said attaching portions, and being moved to an actuated position by any limiting unit attached to any of said attaching portions and being in said operative position, whereby more than one limiting unit can be mounted on said attaching portions for moving said transmitting device, and a limiting valve including a limiting piston operated by said transmitting device in said actuated position to control the flow of fluid in said control valve means so that fluid from said control valve means actuates said power amplifier means to operate said adjusting means to reduce the quantity of fluid transported by said hydraulic machine.
  • Control apparatus as claimed in claim 1, wherein one of said limiting units is a pressure limiting unit, a second limiting unit is a flow volume limiting unit, and a third limiting unit is a torque limiting unit.
  • each of said attaching portions includes a threaded bore; and wherein each of said limiting units includes a body having an outer thread matching the thread of said threaded bores.
  • At least one of said limiting units includes a bore, and a measuring piston in said bore movable between said position of rest and said operative position.
  • a first limiting unit is a pressure limiting unit; wherein a second limiting unit is a flow volume limiting unit; wherein a third limiting unit is a torque limiting unit; wherein said three limiting units are mounted in three attaching portions, respectively,; wherein said transmitting means includes a first transmitting means engaged by said first and second limiting units and operated by the same to displace said limiting piston, and a second transmitting means engaged and operated by said third limiting unit, and operatively connected with said first transmitting means to operate the same to displace said limiting piston.
  • a first limiting unit of said limiting units is a pressure limiting unit including a body forming a cylinder bore and mounted on a first attaching portion, a measuring piston forming in said cylinder bore, a pressure chamber communicating with said hydraulic machine, and a first spring biasing said measuring piston against the pressure of fluid in said pressure chamber; and wherein said measuring piston has a pin portion projecting out of said body for operating said transmitting device.
  • a second limiting unit is a flow volume limiting unit including a second body mounted on a second attaching portion and forming a second cylinder bore, a second measuring piston mounted in said second cylinder bore and forming two second pressure chambers in said second cylinder bore; a high pressure conduit connected with said hydraulic machine; a throttle in said conduit; wherein one of said second pressure chambers receives high pressure fluid from said conduit upstream of said throttle and the other second pressure chamber receives fluid from said conduit downstream of said throttle; and a second spring biasing said second measuring piston; and wherein said second measuring piston has a second pin portion projecting out of said second body for operating said transmitting device.
  • each of said attaching portions of said supporting means includes a threaded bore; wherein said bodies of said first and second limiting units have outer threads threaded into said threaded bores; wherein said first and second springs having ends abutting the bottoms of said threaded bores so that the tension of said springs is adjusted by screwing said bodies into said threaded bores, respectively.
  • said supporting means has an abutment surface; wherein said transmitting device includes a transmitting plate having on opposite ends on the bottom face fulcrum bulges resting on said abutment surface; wherein said pin portions abut said bottom face at said ends; wherein said limiting piston is spring biased toward said transmitting plate and engages the top surface thereof equidistant from said ends whereby when anyone of said pin portions displaces the respective end of said transmitting plate, the same is turned about the fulcrum bulge at the respective other end so that said limiting piston is operated.
  • a third limiting unit is a torque limiting unit having a third body mounted on a third attaching portion of said supporting means and forming a third cylinder bore; a third measuring piston in said third cylinder bore forming a third pressure chamber in the same communicating with said hydraulic machine; wherein said third measuring piston has a third pin portion projecting out of said body for operating said transmitting device.
  • said transmitting device further includes a double armed lever engaged by said third pin portion and having projections at the ends thereof, linkage means controlled by said power amplifier means for moving said lever perpendicularly to the direction of movement of said third pin portion, a lever arm mounted for angular movement about an axis, biasing means for biasing said lever arm to engage said projections, said lever arm having a free end resting on said projections, and means connecting said lever arm with said transmitting plate for operating said limiting valve means.
  • lever arm includes a curved guide track for guiding said piston of said biasing means; and wherein said mounting means support said biasing means for angular movement along said guide track.
  • Control apparatus as claimed in claim 11, comprising a linkage operatively connecting said manually operated setting means with said biasing means for varying the point of engagement of said biasing means with said lever arm.
  • Control apparatus as claimed in claim 11, comprising a combustion motor for driving said hydraulic machine and having a gas pedal; and a linkage operatively connecting said gas pedal with said biasing means for varying the point of engagement of said biasing means with said lever arm.
  • Control apparatus as claimed in claim 11, including shaft means for mounting said lever arm for angular movement; and means for gradually slanting said shaft means.
  • Control apparatus as claimed in claim 11, comprising a vehicle having wheels and supporting said hydraulic machine; said hydraulic machine being a pump; a hydraulic motor driven by said pump and driving said wheels; a friction brake operable for braking said wheels and including a brake pedal; and linkage means connecting said brake pedal with said biasing means for varying the point of engagement of said biasing means with said lever arm.
  • said setting means include first and second linkage means connected with said valve slide and with said power amplifier means, respectively, a manually operated member; and resilient connecting means connecting said first and second linkage means with said manually operated member so that said power amplifier means can adjust said adjusting means under the control of said limiting units without displacing said manually operated member.
  • valve means includes springs acting on the ends of said valve slide for urging the same to a central position.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Reciprocating Pumps (AREA)
  • Control Of Fluid Gearings (AREA)
  • Fluid-Pressure Circuits (AREA)
US00216187A 1971-01-15 1972-01-07 Hydraulic control apparatus for a hydraulic machine Expired - Lifetime US3746115A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE19712101730 DE2101730A1 (de) 1971-01-15 1971-01-15 Regel- und Steuereinrichtung für eine Hydromaschine

Publications (1)

Publication Number Publication Date
US3746115A true US3746115A (en) 1973-07-17

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Family Applications (1)

Application Number Title Priority Date Filing Date
US00216187A Expired - Lifetime US3746115A (en) 1971-01-15 1972-01-07 Hydraulic control apparatus for a hydraulic machine

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US (1) US3746115A (cg-RX-API-DMAC10.html)
DE (1) DE2101730A1 (cg-RX-API-DMAC10.html)
FR (1) FR2121871B1 (cg-RX-API-DMAC10.html)
GB (1) GB1377851A (cg-RX-API-DMAC10.html)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3913698A (en) * 1974-02-01 1975-10-21 Power Matic Corp Variable speed transmission
US4461147A (en) * 1981-10-27 1984-07-24 Sundstrand Corporation Variable displacement hydraulic control with override
US4518320A (en) * 1984-02-03 1985-05-21 Deere & Company Variable displacement pump system
US4518319A (en) * 1984-02-03 1985-05-21 Deere & Company Variable displacement pump system
US20130192918A1 (en) * 2012-01-26 2013-08-01 Caterpillar, Inc. Brake System Having a Brake Capacity Test Mode for a Machine Having a Hydrostatic Drivetrain

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3042837C2 (de) * 1980-11-13 1982-12-09 Hydromatik Gmbh, 7900 Ulm Steuer- und Regeleinrichtung bei einem hydrostatischen Getriebe
CN103758826B (zh) * 2014-01-23 2016-02-03 中国重型机械研究院股份公司 一种大流量泵供液系统

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2257724A (en) * 1936-09-12 1941-10-07 David S Bennetch Transmission
US2516662A (en) * 1946-06-10 1950-07-25 Vickers Inc Power transmission
US2556378A (en) * 1949-03-08 1951-06-12 Sisson Lowell Rotary pump and motor hydraulic transmission
US3633359A (en) * 1969-02-18 1972-01-11 Dowty Hydraulic Units Ltd Hydraulic apparatus
US3672161A (en) * 1970-01-15 1972-06-27 Linde Ag Control system for a stepless hydrostatic drive

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Publication number Priority date Publication date Assignee Title
NL95136C (nl) * 1955-02-03 1960-08-15 Metallwerk Glockerau Gmbh Hydraulisch drijfwerk voor een lier
FR1335540A (fr) * 1962-06-26 1963-08-23 Sigma Perfectionnements apportés aux transmissions hydrostatiques à rapport variable
GB980605A (en) * 1963-08-14 1965-01-13 Bendix Corp Variable displacement pump

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2257724A (en) * 1936-09-12 1941-10-07 David S Bennetch Transmission
US2516662A (en) * 1946-06-10 1950-07-25 Vickers Inc Power transmission
US2556378A (en) * 1949-03-08 1951-06-12 Sisson Lowell Rotary pump and motor hydraulic transmission
US3633359A (en) * 1969-02-18 1972-01-11 Dowty Hydraulic Units Ltd Hydraulic apparatus
US3672161A (en) * 1970-01-15 1972-06-27 Linde Ag Control system for a stepless hydrostatic drive

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3913698A (en) * 1974-02-01 1975-10-21 Power Matic Corp Variable speed transmission
US4461147A (en) * 1981-10-27 1984-07-24 Sundstrand Corporation Variable displacement hydraulic control with override
US4518320A (en) * 1984-02-03 1985-05-21 Deere & Company Variable displacement pump system
US4518319A (en) * 1984-02-03 1985-05-21 Deere & Company Variable displacement pump system
US20130192918A1 (en) * 2012-01-26 2013-08-01 Caterpillar, Inc. Brake System Having a Brake Capacity Test Mode for a Machine Having a Hydrostatic Drivetrain
US9097341B2 (en) * 2012-01-26 2015-08-04 Caterpillar Inc. Brake system having a brake capacity test mode for a machine having a hydrostatic drivetrain

Also Published As

Publication number Publication date
DE2101730A1 (de) 1972-07-20
FR2121871A1 (cg-RX-API-DMAC10.html) 1972-08-25
FR2121871B1 (cg-RX-API-DMAC10.html) 1977-01-14
GB1377851A (en) 1974-12-18

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