US3230715A - Hydraulic-machine system with idling mode - Google Patents

Hydraulic-machine system with idling mode Download PDF

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Publication number
US3230715A
US3230715A US426006A US42600665A US3230715A US 3230715 A US3230715 A US 3230715A US 426006 A US426006 A US 426006A US 42600665 A US42600665 A US 42600665A US 3230715 A US3230715 A US 3230715A
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Prior art keywords
hydraulic
elements
fluid
contour
pump
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Expired - Lifetime
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US426006A
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English (en)
Inventor
Klein Hans-Christof
Budecker Ludwig
Hertell Siegfried
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Continental Teves AG and Co oHG
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Alfred Teves GmbH
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/06—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations specially adapted for stopping, starting, idling or no-load operation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/08—Rotary pistons
    • F01C21/0809—Construction of vanes or vane holders
    • F01C21/0818—Vane tracking; control therefor
    • F01C21/0854—Vane tracking; control therefor by fluid means
    • F01C21/0863—Vane tracking; control therefor by fluid means the fluid being the working fluid

Definitions

  • HYDRAULIC-MACHINE SYSTEM WITH IDLING MODE 2 Sheets-Sheet 1 Filed Jan. 18, 1965 HANS -CHRI8TOF KL IN LUDW/G BUDEC/(ER S/EGFR/ED HERTEL L y Ross 6 Wafer):
  • Our present invention relates to a hydraulicmachine system and, more particularly, to hydraulic machines driven by fluid under pressure orcapable of displacing fluids, as well as a method of operating such systems.
  • hydraulic machine is intended to define a transducer capable of converting mechanical movement into hydraulic displacement (i.e. displacement of a hydraulic fluid under pressure) or of converting fluid pressure intomechani-cal movement.
  • Hydrodynamic and hydrostatic devices of this character include hydraulic motors, pumps and servo systems which generally have at least .one pair of relativelymovable members, one of which is provided with a plurality of variable-working elements (e.g. radial vanes, pistons, slides, valve elements and the like) which 'bear upon the other of the pair of members, the latter member having a contour defining the stroke of the elements.
  • variable-working elements e.g. radial vanes, pistons, slides, valve elements and the like
  • the vanes may form an impeller and co-operate with the contour to define compartments or chambers from whichhydraulic fluid under pressure is displaced and into which further quantities of the hydraulic fluid are drawn as the two members are relatively shifted.
  • the contour may constitute a cam adapted to operate the elements as pistons in, for example, a radial-piston pump or motor.
  • the stroke of the piston elements determines the fluid displacement or, in the case of a motor, the extent of the relative displacement.
  • Many other hydraulic machines are characterized by these three principal structural com- Machines of this type, however, usually reworking elements against the cam or contour carried by the opposing member.
  • the radial-pistons or vanes can be urged against the contour or cam at least in part by centrifugal force.
  • some other pressure means e.g. a resilient or spring means (i.e. coil spring, compression chamber or the like), or the force of a hydraulic fluid derived from some external source.
  • a resilient or spring means i.e. coil spring, compression chamber or the like
  • Another object of this invention is to provide a method of operating a hydraulic machine having variable-stroke working elements in such manner as to prevent'the hydraulic device from retarding or reducing the efficiency of any mechanical device with which it may be coupled.
  • Still another object of this invention is to provide a system incorporating a hydraulic machine of the character described which eliminates the need for a clutch mechanism or the like between the mechanical element and the hydraulic machine when the operational modes are to include an idling condition.
  • additional pressure means are provided during the normal operation of the device for holding the variable-stroke elements against the cam surface or contour end, according to the present invention, the means for hydraulically biasing these ele ments away fromthe contour are dimensioned to at least limitedly counteract the forces applied by such pressure
  • the latter can be resilient means (e. g. coil springs, chambers containing a compressible fluid) or they may involve the use of a hydraulic force when, for example, the variable-stroke elements form pistons reciprocable within variable-capacity compartments.
  • Such compartments can be fed with hydraulic fluid .under pressure during the normal operating mode of the machine,
  • the hydraulic fluid then serving to supplement a resilient means or the centrifugal action of the movable member.
  • the method of the present invention involves the is supplied for reducing the frictional interengagement.
  • the two members define between them at least one fluid chamber in which the working elements bear upon the contour, these elements having, exposed to fluid within this chamber, surfaces generally transverse to the direction of stroke, i.e. transverse to the direction in which they are normally hydraulically, resiliently and/ or centrifugally biased.
  • the means for urging the elements away from the contour can include a source of fluid pressure and control means (e.g. a multi-position or distributing valve) connecting the source of fluid pressure with this chamber so as to expose these surfaces to fluidin the idling condition of the machine whereby the elements are displaced away from the surface which they normally bear against.
  • the present invention is thus applicable to hydraulic machines employing radial-piston elements, radial vanes, valves, sliding partitions, and other devices movable inwardly and outwardly and disposed either upon the rotor or upon the stator.
  • the pressure supplied by the source adapted to bias the elements away' from the contour must be so great that at least part and preferably all of the force tending to urge them into contact with the contour is counterbalance-d and, even more advantageously, is sufficient to displace theelements from any contact whatsoever with the contour.
  • the dual-pump means can include a low-capacity pump constituting the source of fluid pressure designed to urge the variable-stroke elements away from the contour, and a high-capacity pump communicating with both the compartments in which the radial vanes or elements are shiftable as pistons and the compartments defined between the radial vanes and the relatively rotatable motor members.
  • the control means can thus be a two-position valve which, in a first or normal position, connects the high-capacity pump with both the working compartments and the variable-capacity compartments or cylinders, whereas, in a second operative position (idling condition) the output of the high-capacity pump is returned to a reservoir. In this second position, the output of the low-capacity pump feed only those working compartments which, in this case, constitute the fluid chamber in which the surfaces of the working elements are exposed to the fluid.
  • a check-valve means is preferably interposed between the low-capacity pump and the highcapacity pump, these means being oriented to prevent the flow under pressure from the low-pressure pump to the reservoir in the second operative position of the control means.
  • control means in this second operative position, is, according to a still more specific feature of the invention, so designed as to divert hydraulic fluid from the variable-capacity compartments or cylinders to a reservoir from which the dual-pump means draws hydraulic fluid.
  • the control means can include a manually-operable two-position valve, or one which is responsive to fluid pressure in this systerrn to the rotational speed of the mechanical device or the hydraulic machine, or some still more remote means to which the system is to respond.
  • the hydraulic pump is the kinematic reversal of a hydraulic motor, when they present invention is applied to such a pump, the discharge side or outlet of the rotaryvane machine must be blocked while the intake or suction side is supplied with fluid under pressure from a suitable source, e.g. one of the hydrostatic pumps mentioned above.
  • FIG. 1 is an axial cross-sectional view, in idealized form, of a hydraulic motor, according to the present invention, the remainder of the hydraulic system being shown diagrammatically;
  • FIG. 2 is a cross sectional view taken along the line IIII of FIG. 1.
  • FIGS. 1 and 2 there is illustrated a hydraulic machine which, for the purpose of this description, can be a rotary-piston or rotary-vanehydraulic motor.
  • the motor 1 comprises a housing 6 in which an apertured flowcontrol plate 5 is received, this plate being provided with an annular inlet bore or passage 4 in communication with the inlet opening 4' of housing 6.
  • annular member 10 constituting a cam and formed with the contour 10 which defines the stroke of the radial vanes 8 carried by the rotor 9.
  • the rotor 9 has an internally splined hub 9 in which the splined shaft 9" of a load 30 is received for rotatable entrainment.
  • the hub 9 is mounted in the bearings 31 which, in turn, are bracketed by seals 32, 33 to prevent the escape of fluid between the housing 6 and the rotor 9.
  • each of the radial vanes 8 is slidably guided in the rotor 9 and is biased by springs 13 against the contour surface 10' of the annular cam 10.
  • each of the radial vanes 8 is slidable in a variable-capacity compartment 2% which, in the region of the kidney-shaped 'inlet apertures 7, register with similar apertures 14 of the control plate 5, apertures 14 being supplied with fluid via a duct14 and the fluid line 15.
  • the control plate 11 is provided with kidney- .shaped outlet apertures 25 which remove fluid from com partment 20 and conduct it to the duct 25 with which hydraulic line 19 communicates.
  • the control plate 11 is formed with an annular passage 17, similar to that shown at4, communicating with the kidney-shaped apertures 16 and leading hydraulic fluid out of the motor via an outlet 17. Seals 11' and 11 serve to prevent the escape of hydraulic fluid between the axially extending flange 11a and the housing 6. Axially extending bolts 34 draw the bipartite housing 6, the control plates 5, l1 and the cam 10 together, the rotor 9 being disposed between the control plates.
  • the remainder of the hydraulic system includes a dualpump means, generally designated 3, including a lowcapacity hydrostatic pump 3b which supplies fluid via a line. 2 to the inlet 4.
  • the large-capacity hydrostatic pump 3a communicates with a two-position valve 22 of the control means which feeds the line 15 to which hydraulic line 15 is connected.
  • a check valve 24 interconnects line 2 and line 15'.
  • the dual-pump means 3 is supplied with hydraulic fluid from a reservoir 23 to which the valve 22 returns hydraulic fluid via the line 23when the valve connects this line with the return pipe 18.
  • the fluid circuit is thus established between the -pump means 3, the control valve 22, the inlet side of the hydraulic motor 1, the radialvanes and chambers defined thereby, the outlet side of the hydraulic motor, the return line 18, the valve 22 and the reservoir 23.
  • the lg lrauli'c fluid large-capacity pump 3a is diverted to the reservoir 23 with which the hydraulic motor is connected as will become apparent hereinafter.
  • the valve 22 may be controlled by the manual operating means diagrammatically represented .at 35 or a tachometer 36 responsive to the rotary speed of the shaft 9 coupled with the load 30; a pressure-responsive device may also be provided for operating-this valve.
  • hydraulic fluid is drawn by both pumps 3a and 312 from the reservoir 23.
  • The-output from pump 3a passes via the valve 22, in the indicated operative position, through line 15' and conduit 15 whence it enters the housing 6 and passes into duct 14 and thence through apertures 14- into the variable-capacity compartments 2d where it assists or supplements the springs 13 in the region of the aperture 7 in urging the radial vanes 8 against the cam-10.
  • the flow-hydraulic fluid through line 2 is, however, .at a low rate so that additional fluid passes via the check valve 24 to line 2 whence it enters inlet 4.
  • the hydraulic fluid entering duct 4 then proceeds through the through the outlet apertures 16, the duct 17 and outlet 17' whence the fluid again proceeds via valve 22 to line 23 and the reservoir 23.
  • the rotor 9 thereby drives load 30, the radial vanes 8 being shifted inwardly as they approach the regions between the interleaved apertures 7 and 16. In these regions,'hydraulic pressure does not retard the movement of the vanes since their variable-capacity compartments register with the kidney-shaped openings and discharge fluid through duct 25 and line 19 past the check valve 21 into the return line 18.
  • Check valve 26 remains blocked by the elevated pressure Within line 15".
  • the output of the high-capacity pump 3a is returned to the reservoir 23 through 23' while line 15' likewise communicates with the reservoir.
  • Line 18 is blocked by the valve 22.
  • the auxiliary or low capacity pump 3b supplies hydraulic fluid via line 2 to the inlet 4'.
  • the check valve 24 prevents transmission of fluid from line 2 to line 15'.
  • the fluid entering duct 4 passes via apertures 7 into the working compartments 37 whence it bears upon the surfaces '8 of the radial vanes 8 extending transversely to the direction of stroke (i.e. the radial direction).
  • the elevated fluid pressure in chamber 37 thus biases the radial vanes 8 inwardly and withdraws them from engagement with the cam 10, the pressure of low-capacity pump 3b being suflicient to counteract the force of springs 13 urging each of these radial vanes 8 outwardly. Since pump 3a no longer supplies fluid under pressure to line 15, the pressure within chambers 37 is sufficient to displace the radial vanes 8 and discharge the fluid within the variable-capacity compartments 2%) through the ducts 14 and 25 to the lines 15 and 1?, respectively.
  • the fluid forced through line 15 returns to the reservoir 23 via the valve 22 whereas that passing through line 19 cannot enter the blocked line 13 but flows past the check valve 26 into the line 15" which is now at reduced pressure.
  • a relief valve 27 is provided to regulate the pressure within ducts 4 and 17 and within the compartments 37. When the pressure within these compartments exceeds that required to hold the radical vanes 8 out of engagement with the cam 10, the valve 27 opens to discharge fluid and restore the desired pressure.
  • step (b) hydraulically biasing said elements away from said contour in an idling condition of the machine against the forces urging the elements in the direction of the contour by supply fluid under pressure to said chambers while terminating the supply of fluid in step (a), thereby reducing frictional interengagement of said members during said idling condition.
  • a hydraulic system comprising a hydraulic machine having a pair of relatively movable members, a plurality of variable-stroke working elements entrained by one of said members and bearing upon the other of said members, said other of said members having a contour defining the stroke of said elements, and means including said elements and at least one of said members forming working compartments for a hydraulic fluid; and means for hydraulically biasing said elements in an idling condition of said machine against the forces urging the elements in the direction of said contour.
  • said members define between them at least one fluid chamber in which said elements bear upon said contour, said elements having in said chamber surfaces generally transverse to their direction of stroke, said means for hydraulically biasing said elements including a source of fluid pressure and control means connecting said source with said chamber in said idling condition of said machine.
  • a system as defined in claim 4 wherein said member entraining said elements is a rotor and said elements bear upon said other member with centrifugal force, said source and said control means being so dimensioned as to supply fluid pressure to said chamber in said idling conditions of said machine of a magnitude suflicient at least to balance part of the centrifugal force holding said elements against said contour.
  • a system as defined in claim 4 wherein said member entraining said elements is provided with pressure means urging said elements into contact with said contour under said forces, said source and said control means being so dimensioned as to supply fluid pressure to said chamber in said idling condition of said machine of a magnitude suflicient at least to balance part of said forces.
  • said pressure means includes spring means urging said elements in the direction of said contour.
  • said pressure means includes variable-capacity compartments formed in the member entraining said elements and receiving same, and means for supplying hydraulic fluid under pressure to said variable-capacity compartments.
  • a system as defined in claim 8 wherein said means for hydraulically biasing said elements includes means for connecting said variable-capacity compartments to a fluid reservoir.
  • a hydraulic system comprising a radial-vane hydraulic motor including a rotor, a plurality of radially shiftable vanes mounted on said rotor, spring means on said rotor urging said vanes radially outwardly, a stator surrounding said rotor and formed with an annular cam for regulating the stroke of said vanes and defining with said rotor and with said vanes a plurality of working chambers, inlet means for supplying hydraulic fluid under pressure to certain of said chambers, outlet means for removing hydraulic fluid from others of said chambers, said radial vanes each defining with said rotor a respective variable-capacity compartment, means for supplying fluid under pressure to said compartments, thereby urging said vanes into engagement with said cam in aiding relationship with said springs, means for leading fluid away from said compartments upon inward displacement of said vanes by said cam; dual-pump means including a relatively low-capacity pump and a relatively high-capacity pump; control-valve means interposed between said dual-pur

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
US426006A 1964-01-24 1965-01-18 Hydraulic-machine system with idling mode Expired - Lifetime US3230715A (en)

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DET0025480 1964-01-24

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DE (1) DE1553224A1 (es)
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SE (1) SE333874B (es)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3700363A (en) * 1971-02-04 1972-10-24 Gardner Denver Co Low inertia motor for fluid operated tool
DE2350038A1 (de) * 1972-11-02 1974-05-16 Deere & Co Hydrostatischer zusatzantrieb fuer kraftfahrzeuge, insbesondere ackerschlepper
US3815478A (en) * 1970-06-26 1974-06-11 Caterpillar Tractor Co Pipelayer hydraulic drawworks with free-fall

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4303115A1 (de) * 1993-02-04 1994-08-11 Bosch Gmbh Robert Flügelzellenpumpe
GB2287756B (en) * 1994-03-19 1998-04-08 Acg France Rotary vane pump

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2719512A (en) * 1951-03-15 1955-10-04 Pixley Truck Sales Company Power transmitting devices
US2777396A (en) * 1953-05-15 1957-01-15 American Brake Shoe Co Fluid energy translating device
US3076414A (en) * 1958-04-21 1963-02-05 American Brake Shoe Co Fluid pressure energy translating devices

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2719512A (en) * 1951-03-15 1955-10-04 Pixley Truck Sales Company Power transmitting devices
US2777396A (en) * 1953-05-15 1957-01-15 American Brake Shoe Co Fluid energy translating device
US3076414A (en) * 1958-04-21 1963-02-05 American Brake Shoe Co Fluid pressure energy translating devices

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3815478A (en) * 1970-06-26 1974-06-11 Caterpillar Tractor Co Pipelayer hydraulic drawworks with free-fall
US3700363A (en) * 1971-02-04 1972-10-24 Gardner Denver Co Low inertia motor for fluid operated tool
DE2350038A1 (de) * 1972-11-02 1974-05-16 Deere & Co Hydrostatischer zusatzantrieb fuer kraftfahrzeuge, insbesondere ackerschlepper
FR2205862A5 (es) * 1972-11-02 1974-05-31 Deere & Co
US3823650A (en) * 1972-11-02 1974-07-16 Deere & Co Destroking of hydrostatic drive motors

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GB1091333A (en) 1967-11-15
DE1553224A1 (de) 1969-11-06
SE333874B (es) 1971-03-29

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