US3662551A - Fluid pressure controlling - Google Patents

Fluid pressure controlling Download PDF

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US3662551A
US3662551A US65102A US3662551DA US3662551A US 3662551 A US3662551 A US 3662551A US 65102 A US65102 A US 65102A US 3662551D A US3662551D A US 3662551DA US 3662551 A US3662551 A US 3662551A
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fluid
pressure
chamber
valving
outlet
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James M Denker
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Nutron Corp
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Nutron Corp
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B3/00—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F01B3/0032—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
    • F01B3/0044—Component parts, details, e.g. valves, sealings, lubrication
    • F01B3/0064—Machine housing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B3/00—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F01B3/0032—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
    • F01B3/0035—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block having two or more sets of cylinders or pistons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B3/00—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F01B3/04—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis the piston motion being transmitted by curved surfaces

Definitions

  • a third Primary xaminerEdgar W. Geoghegan Attorney-Wm. W. Rymer aspect in which a second chamber surrounds the shaft on which the rotor is mounted, that improvement wherein the annular chamber is maintained at one pressure level and fluid in the second chamber is maintained at a second, significantly lower pressure level.
  • a principal object is to eliminate stuttering or jumping of pistons on their track during rotation of the device.
  • a principal object of a third aspect is to eliminate the need for high pressure shaft seals.
  • Other objects include providing during working of the device an outward piston bias force that is either constant or bears a predetermined relationship to one of the working fluid pressures, and providing an override for causing free-wheeling of the device.
  • the invention features, in a rotary fluid device of the type comprising two elements. one of which is capable of operation as a fluid pump and the other of which is capable of operation as a fluid motor, and which are coupled to a common shaft, the motor element having the inlet thereof adapted for communication with the main inlet of the device and the outlet thereof adapted for communication with an intermediate conduit, the pump element having the inlet thereof adapted for communication with the intermediate conduit and the outlet thereof adapted for communication with the main outlet of the device, that improvement comprising ducting extending from the intermediate conduit to a fluid drain, and valving within the ducting and responsive to fluid pressure within one of the main inlet and main outlet for maintaining the fluid in the intermediate conduit at a pressure bearing a predetermined relationship to the pressure of fluid in the one.
  • a device having valving and ducting as above described and in which the elements are pistons carried by a rotor mounted within a housing and the intermediate conduit is an annular chamber intermediate the rotor and housing in which the pistons are located during rotation of the rotor.
  • the invention features maintaining the annular chamber at one pressure level and maintaining a second chamber surrounding the shaft on which the rotor is mounted at a significantly lower, preferably substantially atmospheric, pressure level.
  • Preferred embodiments feature, in devices including all three aspects and in which the elements are capable of operation as pumps and motors, maintaining the pressure in the annular chamber a predetermined amount below the lesser of the pressure levels of the main inlet and main outlet and providing override means for maintaining the annular chamber pressure level at a level not less than that of the pressure level of a selected one of the main inlet and main outlet.
  • FIG. I is a longitudinal cross-sectional view of a rotary fluid motor constructed in accordance with the present invention.
  • FIG. 2 is a partial transverse cross-section of the motor of H6. 1 taken at 22 ofFlG. 1;
  • FIG. 3 is a partial longitudinal cross-section of the motor of FIG. I taken at 33 of FIG. 2;
  • FIG. 4 is a longitudinal sectional view of a pressure control valve of the motor of FIG. 1;
  • FIG. 5 is a longitudinal sectional view of a second form of pressure control valve
  • FIG. 6 is a longitudinal sectional view of a third form of pressure control valve.
  • FIG. 7 is a diagrammatic view of a fluidcontrol circuit useful with the motor of FIG. 1.
  • a rotary fluid motor comprising an output shaft 12 extending coaxially through a rnulti-part housing including, in coaxial alignment, a cylindrical main housing 14, a cylindrical support housing section 16 and end plate 18. At one end of the housing, output shaft 12 is journaled within a roller bearing 20 (whose inner face engages the shaft periphery and whose outer face engages the inner wall of housing section 14); and
  • shafi 12 is journaled within a ball bearing 22 (whose inner face engages the shaft periphery and whose outer face engages the inner wall of housing section 16. Rubber lip seals 24, 26 are provided intermediate and prevent leakage between shaft 12 and, respectively, housing section 14 and end plate 18.
  • a stepped cylindrical fluid distribution manifold 30 and rotor 34 are mounted within annular cavities within main housing 14 and surrounding shaft 12.
  • One axial face 35 of rotor 34 is in face-to-face engagement with the adjacent face 31 of manifold 30.
  • a wave washer 32 engages the other axial face 33 of manifold 30 and the portion of main housing 14 defining the adjacent end wall of the cavity.
  • Rotor 34 is fixed on shaft 12 for rotation therewith by spline 40.
  • housing 14, manifold 30 and housing section 16 are of slightly greater diameter than are the portions of the outer peripheral surface of shaft 12 they respectively surround, thereby providing an annular chamber 38 about the shaft. Communication between the portions of chamber 38 on opposite sides of rotor 34 is provided by interstitial passages of spline 40.
  • Main housing 14 includes drilled inlet, outlet, main drain and shaft drain conduits, designated 56, 57, 58 and 59, respectively, extending through the wall of the main housing section. The outer portion of each conduit is tapped for receiving fluid couplings.
  • a pair of axially spaced, radially inwardly facing annular channels 62, 64 are provided in housing section 14 at the periphery of manifold 30.
  • Inlet conduit 56 communicates at its inner end with channel 62
  • outlet conduit 57 communicates at its inner end with channel 64.
  • Shaft conduit 59 communicates at its inner end with the annulus in which wave washer 32 is mounted.
  • An annular chamber 66 defined by an annular seal 68 and adjacent portions of manifold 30 and housing section I4, surrounds manifold 30 adjacent the annular surface 67 thereof facing but spaced from rotor 34, with surface 67 providing one end wall of chamber 66.
  • Seal 68 comprises an aluminum ring having radially inwardly and outwardly facing circumferential recesses in which are mounted O-rings.
  • a drilled conduit 69 extends from chamber 66 through the radial thickness of manifold 30 to chamber 38.
  • Rotor 34 includes a total of ten cylindrical bores and 10 cylindrical conduits 82 (arranged in a ring within the rings of bores 80) extending axially through the full thickness of the rotor. The bores and ports of each ring are evenly spaced about the circumference of the ring with one port 82 and one bore 80 from each of the two rings in radial alignment.
  • the ring of ports 82 of rotor 34 and of conduits 72, 74 of manifold 30 are of equal diameter.
  • a drilled conduit 84 extends from each port 82 to the bore 80 aligned therewith.
  • Two steel balls 86 are fitted within each of bores 80 for movement within the bore.
  • annular chamber 70 of substantially U- shaped cross-section and defined by adjacent surfaces of rotor 34, housing 14 and housing section 16, surrounds the portion of rotor 34 including bores 80 and balls 86.
  • An annular wave cam 88, 89 including circular undulating ball-engaging surface 90, 91 is mounted on each axial side of rotor 34, coaxially therewith, with the ball-engaging surfaces 90, 91 of each cam engaging one of the balls 86 in each bore 80.
  • Each ball-engaging surface 90, 91 is a trapezoidal acceleration cam surface comprising alternating parabolic and intermediate fairing sections.
  • the period of the cam is 60 (that is, each entire annular surface includes 6 substantially identical complete cycles each having one high point or peak and one low point or valley) and its total amplitude (peak-to-valley) is slightly less than onehalf the diameter of one of balls 86.
  • the high points of each are aligned midway between conduits 72 and 74. Pins 92 hold each cam in position relative to the housing,
  • a cylindrical duct 94 in which is provided a control valve 96, extends from chamber 70 through the lower portion of main drain conduit 58 to a gallery 98 connected to and extending radially outwardly from channel 64.
  • a second, identical, duct 100 in which is provided an identical control valve 101, extends (circumferentially spaced 30 from duct 94) from chamber 70 through main drain conduit 58 to a gallery (not shown) connected to and ex tending outwardly from channel 62.
  • Control valve 96 see FIG.
  • a coaxial cylindrical recess 110 extends most of the length of piston 108, terminating at axial end wall 112 at the end of piston 108 nearest end wall 104.
  • An inlet opening 114 and a damping orifice 116 extend coaxially through end walls 104, 112, respectively.
  • a cylindrical pin 118 one end of which engages seat 106, is movably fitted partially within recess 110.
  • a helical spring 120 within recess 110 engages end wall 112 and the adjacent end of pin 118.
  • Openings 122 spaced circumferentially at 90 intervals, extend through the side wall of body 102 at a distance slightly greater than the overall length of piston 108 from end wall 104. At least two of openings 122 communicate with drain conduit 58.
  • Seat 106 comprises a cylinder which has been relieved, along opposite sides thereof, for about one-half its length, the relieved sections 123 being in cross-section circular segments.
  • a drilled hole 124 extends, from the unrelieved end ofthe seat, approximately four-fifths the overall length of the seat, connecting with the relieved portions and leaving, at the end of seat 106 nearest piston 108, a diametrically extending bar 126 engaging pin 118.
  • fluid is introduced, at high pressure (typically l ,000 p.s.i.), into the motor through conduit 56 and exits from the motor, at low pressure (typically about 500 p.s.i. through conduit 57.
  • a power stroke of the balls 86 within a bore 80 commences when the balls engage a crest or high point of the ball-engaging surfaces 90, 91 of wave cams 88, 89 and, therefore, are in their nearest relative position. With the balls in this position, the rotor port 82 associated with the bore communicates with the end of the conduit 72 that is adjacent to the high point of wave cam 89.
  • High pressure fluid from inlet conduit passes from the inlet through annular channel 62, conduits 72 of manifold 30, rotor port 82 and rotor conduit 84 into the bores 80, thereby forcing the balls within the bore away from each other against the ball-engaging surfaces 90, 91 of wave cams 88, 89.
  • the force of the balls against the ballengaging surfaces imparts a torque to and causes rotation of rotor 34.
  • balls 86 roll down the slopes of the ball-engaging surfaces with which they are in contact, the balls within each bore 80 thereby moving apart.
  • rotor port 82 moves out of communication with conduit 72 and into communication with adjacent conduit 74 in manifold 30.
  • Conduit 74 is connected, through channel 64 to low pressure fluid outlet conduit 57.
  • balls 86 roll up the slopes of ballengaging surfaces 90, 91 thereby moving together and discharging fluid from the bore 80 into the outlet.
  • control valves in ducts 94, 100 maintain the leakage fluid in chamber 70 at a pressure, P that is a predetermined amount below the lesser of the pressures P,, P, of the fluid in chambers 62 and 64 respectively, so that balls 86 will always be biased outwardly against surfaces 90, 91.
  • control valve 96 is open when, as viewed in FIGS. 3 and 4, piston 108 has moved all the way to the right, permitting fluid in chamber 70 to flow through hole 124 in seat 106 and, exiting from valve 96 through the openings 122 communicating with connecting duct 58, the main drain.
  • valve 96 will maintain a difierential between pressure P and the lesser of pressures P, and P, that depends only on the force exerted by spring 120. If, as in the preferred embodiment, the desired differential is 50 psi, the spring is chosen so that it, when the valve opens, exerts a force F equal to 50 times the area, in square inches, of the end of piston 108 surrounding pin 118.
  • control valve connected to the greater of pressures P,, P will at all times be closed.
  • channel 62 is always connected to high inlet pressure, duct 100 and the control valve 101 therein may be eliminated. Provision of a control valve in ducts leading to each of the channels 62, 64, however, makes the motor completely reversible.
  • FIG. 7 diagrammatically illustrates a preferred fluid control circuit useful with motor 10.
  • high pressure fluid from pressure source flows through a four-way, two-position valve and an infinitely adjustable, three-position, four-way valve 157 to the line 154 connected to high pressure inlet conduit 56; and returns from motor 10, at lower pressure, to reservoir 152 through line 156, valve 157, and back-pressure check valve 188.
  • a pair of cross-over pressure relief valves 16], 163 are connected in parallel, in opposed relationship, between lines 154, 156 to maintain the pressure differential between the lines at or below a predetermined level, in the preferred embodiment 1,250 p,s.i.d.
  • a 50 p.s.i.g. pressure reducing valve 173 is mounted in a line extending from the junction between the check valve 165, 167 to the high pressure supply line 151 up stream of valve 157.
  • a check valve 175 is connected in parallel with valve 173 to bypass reverse flow around valve 173 when check valves 165, 167 are piloted to the open condition.
  • a drain line 181 extends from drain conduit 59 to a sump 183, generally one and the same as reservoir 152.
  • a control line 176 in which a check valve 177 and a restriction 187 (O.l g.p.m. nominal flow at 1,250 p.s.i.d.) are mounted in parallel, extends from motor main drain 58 to a port 179 of valve 155.
  • a second control line 169 extends from the pilot connection of check valves 165, 167 to control line 176, upstream of valve 177 and restriction 187.
  • Valve 155 is connected to main reservoir 152 through line 185.
  • a 1,250 p.s.i.g. system relief valve 186 is provided between line and high pressure line 195 upstream of valve 155.
  • a back pressure check valve 188 is provided in the line extending from valve 157 to line 185.
  • a high speed fluid motor 194 or if desired a pressure relief valve (not shown), is connected by lines 190 and 192 respectively, to line 185 and port 179.
  • valve 157 also permits the flow rate, for either direction of rotor rotation, to be varied continuously between no-flow and full-flow.
  • FIG. 6 illustrates another form of control valve 160 for maintaining chamber 70 at a pressure which is a predetermined number of psi below the lesser of pressures P P
  • Control valve 160 comprises a tubular body 162, each end of which is closed by end plugs, designated 164, 166 respectively, and within which a circular in cross-section plunger is coaxially mounted for movement axially within body 162.
  • a drilled opening 170 extends through plug 164; a stepped cylindrical opening having inner portion 172 of diameter equal to that of opening 170 and outer lesser diameter portion 174 extends coaxially through plug 166.
  • a cylindrical stem portion 178 of the plunger is slip-fitted within opening portion 172.
  • the conical head 180 of the plunger is of diameter slightly greater than that of opening 170.
  • a helical spring 182 surrounds the head 180 and a portion of the plunger body, one end of the spring engaging the inner surface of plug 164 and the other end of the spring engaging an annular stop ring portion 184 of the plunger.
  • Valve 160 is closed when head 180 is seated over opening 170 and, as the cross-sectional areas of opening 170 and stem 178 are equal, operates to maintain a differential between pressure P: and the lesser of pressures P,, P, that depends only on the force exerted by spring 182.
  • control valve 130 (see FIG. 5) is substituted for the control valves 96 and 101 in ducts 94, 100.
  • Control valve 130 comprises a tubular body 132 each end of which is closed by end plugs 134, 135 and through the cylindrical wall of which four equally circumferentially spaced drain openings 138 extend.
  • a drilled opening 140 extends through plug 134; a stepped circular opening having inside greater diameter portion 142 and outer lesser diameter portion 144, extends through plug 136.
  • a ball 146 is mounted within body 132 intermediate plugs 134, 136; and a pin 148, one end of which engages ball 146, is movably fitted within portion 142 of plug 136.
  • Valve 130 is closed when ball 146 is seated over opening 140, and is open when ball 146 is spaced from plug 134.
  • the valve operates to maintain pressure P at such a level that:
  • Chamber 38 is connected to an atmospheric pressure sump (not shown) through conduit 59, and the pressure of fluid in chamber 38, and in chamber 66 which is connected to it through conduit 69, is substantially zero.
  • each of balls 86 alternatively acts as a motor driving piston (during the period of time when the bore 80 of the respective piston is connected to high pressure inlet conduit 56 and the high pressure fluid forces the piston outwardly against its respective cam 90, 91, thereby causing rotation of rotor 34), and as a pumping piston (during the period of time when the bore is connected to low pressure outlet conduit 57 and the respective cam 90, 91 forces the ball inwardly into its bore).
  • motor driving the outward movement of the ball 86 forces fluid from the outer portion of the respective bore 80 into chamber 70; during pumping, fluid flows from chamber 70 into the respective bore 80.
  • chamber 70 acts as a conduit between the outlet of the motor driving ball and the inlet of the pumping ball.
  • the inlet of the motor driving ball is, of course, connected to inlet 56, and the outlet of the pumping ball is connected to outlet 57.
  • the operation of the entire motor is substantially equivalent to that produced by coupling two differential elements (such as gear or gerotor motors) to a common shaft (here shafi 12), connecting the inlet of one element to the main fluid inlet (here inlet 56), connecting the outlet of the other element to the main fluid outlet (here outlet 57), and providing controlled pressure intermediate conduit (here chamber 70 the fluid pressure in which is controlled by the ducting and valving previously described) to which the outlet of the one element and the inlet of the other element are connected.
  • all elements are capable of operation as either pumps or motors.
  • the element whose inlet is connected to the main inlet must be capable of operation as a motor and the element whose outlet is connected to the main outlet must be capable of operation as a pump. it reversibility is desired, both elements must be capable of operation, as in the disclosed motor, as either pumps or motors.
  • a fluid device of the type including within a housing an output shaft, a cam and a rotor mounted coaxially of the shaft for relative rotation, a plurality of pistons engaging the cam carried by the rotor for movement relative thereto, fluid means including a fluid inlet and a fluid outlet for selectively forcing the pistons against the cam to cause relative rotation of the cam and rotor, and an internal chamber defined by adjacent portions of the device generally surrounding portions of the rotor carrying the pistons and portions of the cam engaging the pistons, that improvement comprising:
  • valving within said ducting and responsive to fluid in one of said fluid inlet and said fluid outlet for permitting fluid flow from said chamber to said drain when the pressure of fluid within said chamber is greater than a pressure bearing a predetermined relationship to the pressure of said fluid within said one, and preventing said fluid flow when said pressure of said fluid within said chamber is not greater than said pressure bearing a predetermined relationship.
  • first and second differential elements each capable of operation as one of a fluid motor and a fluid pump
  • said first element having the inlet thereof adapted for communication with said main inlet and the outlet thereof adapted for communication with said intermediate conduit
  • said second element having the inlet thereof adapted for communication with said intermediate conduit and the outlet thereof adapted for communication with said main outlet, and,
  • a controller responsive to fluid in one of said main inlet and said main outlet for regulating fluid flow from said intermediate conduit to said drain to maintain the pressure of fluid within said intermediate conduit at a pressure level bearing a predetermined relationship to the pressure of said fluid within said one.
  • the apparatus of claim 2 comprising a device wherein said member is an output shaft and including a cam and a rotor mounted coaxially of the shaft for relative rotation, each of said elements being a piston engaging the cam and carried by the rotor for movement relative thereto, and said conduit being an internal chamber defined by adjacent portions of the apparatus generally surrounding the portions of the rotor carrying the pistons and the portions of the cam engaging the pistons.
  • said controller includes valving within said ducting and responsive to fluid in one of said inlet and said outlet for permitting fluid flow from said chamber to said drain when the pressure of fluid within said chamber is greater than a pressure bearing a predetermined relationship to the pressure of said fluid in said one, and preventing said fluid flow when said pressure of said fluid within said chamber is not greater than said pressure bearing a predetermined relationship.
  • said valving includes a valving mem ber movable between a first position wherein said valving permits said flow and a second position wherein said valving prevents said flow and a spring engaging said valving member and exerting thereupon a force tending to move said member towards said first position, said valving member defining a pair of oppositely facing valving surfaces, the effective area of each of said surfaces projected on planes perpendicular to the direction of movement of said member being equal.
  • said valving includes a tubular body member having at least one port in the circumferential surface thereof, and said valving member is mounted within said body member, said valving member being positioned over said port in said second position and being spaced from said port in said first position.
  • valving surfaces are annular and lie in planes perpendicular to said direction.
  • said valving includes a valving member movable between a first position wherein said valving permits said flow and second position wherein said valving prevents said flow and defines a pair of generally oppositely facing valving surfaces, the ratio of the effective areas of said surfaces projected on planes perpendicular to the direction of movement of said member being equal to said predetermined fraction.
  • the device of claim 5 including valving responsive to each of said fluid inlet and said fluid outlet for permitting said fluid flow when said pressure within said chamber is greater than a pressure bearing a predetermined relationship to the lesser of the pressure of fluid within said inlet and the pressure of fluid within said outlet.
  • the device of claim 14 wherein said device defines a first valving conduit extending from said chamber to said inlet, a second valving conduit extending from said chamber to said outlet, each of said valving conduits communicating with said drain, and a valve within each of said conduits, each of said valves being responsive to the pressure of fluid in the respective one of said inlet and outlet for permitting fluid flow through said each valve to said drain when said pressure in said chamber is greater than a predetermined number of psi below the pressure of fluid in said respective one.
  • valves comprises a tubular body member having at least one port in the cylindrical wall thereof, a valving member mounted therein for movement between a first position spaced from said port and a second position overlying said port, and a spring engaging said valving member and exerting thereupon a force tending to move said valving member towards said first position, said valving member defining a pair of oppositely facing valving surfaces, the effective area of each of said surfaces projected on planes perpendicular to the direction of movement of said valving member being equal.
  • each of said valving conduits communicating with said drain, and a valve within each of said conduits, each of said valves being responsive to the pressure of fluid in the respective one of said inlet and outlet for permitting fluid flow through said each valve to said drain when said pressure in said chamber is greater than a predetermined fraction of the pressure of fluid in said respective one.
  • valves comprises a tubular body member having at least one port in the cylindrical wall thereof and a valving member movable between a first position wherein said valve permits flow from said chamber to said drain and a second position when said valve prevents flow from said chamber to said drain, said valve defining a pair of generally oppositely facing surfaces, the ratio of the effective areas of said surfaces projected on planes perpendicular to the direction of movement of said member being equal to said predetermined fraction.
  • a fluid device of the type including within a housing an output shaft, a cam and a rotor mounted for relative rotation coaxially of the shaft, a plurality of pistons engaging the cam carried by the rotor for movement relative thereto, and fluid means including a fluid inlet and a fluid outlet for selectively forcing the pistons against the cam to cause relative rotation of the cam and rotor, that improvement wherein:
  • said shaft and adjacent portions of said device define a first generally annular chamber extending coaxially of said shafi, at least one end portion of said first chamber being defined by an annular seal surrounding said shaft, adjacent portions of said housing, rotor and other components of said device define a second generally annular chamber generally surrounding portions of said rotor carrying said pistons and portions of said cam engaging said pistons;
  • said device includes means for maintaining fluid in said first chamber at a level of pressure substantially less than the pressure of fluid in said second chamber during working of said device.
  • said means includes first chamber ducting connecting said first chamber to a drain outlet, said drain outlet being maintained at a level of pressure that is less than the pressure of fluid within said inlet and outlet.
  • said means includes second chamber ducting extending from said second chamber to a drain outlet and a valve within said second chamber ducting responsive to fluid in one of said inlet and outlet for permitting fluid flow from said second chamber through said valve when the pressure of fluid within said second chamber is greater than a pressure bearing a predetermined relationship to the pressure of fluid within said one and preventing said flow when said pressure of fluid within said chamber is less than pressure bearing a predetermined relationship.
  • valve permits said flow when said pressure within said chamber is greater than a predetermined number of psi below said pressure of fluid in said one.
  • valve includes a valving member movable between a first position wherein said valve permits said flow and a second position wherein said valve prevents said flow and a spring engaging said valving member and exerting thereupon a force tending to move said member towards said first position, said valving member defining a pair of oppositely facing valving surfaces, the effective area of each of said surfaces projected on planes perpendicular to the direction of movement of said member being equal.
  • valve permits said flow when said pressure within said second chamber is greater than a predetermined fraction of said pressure of fluid in said one.
  • valve includes a valving member movable between a first position wherein said valve permits said flow and a second position wherein said valve prevents said flow and defines a pair of generally oppositely facing valving surfaces, the ratio of the effective areas of said surfaces projected on planes perpendicular to the direction of movement of said member being equal to said predetermined fraction.
  • the device of claim 5 including override means for maintaining the pressure of fluid in said chamber at a level of pressure not less than the pressure of fluid in a selected one of said inlet and said outlet.
  • fluid device of the type including within a housing an output shaft, a cam and a rotor mounted coaxially of the shaft for relative rotation, a plurality of pistons engaging the cam carried by the rotor for movement relative thereto, fluid means including a fluid inlet and a fluid outlet for selectively forcing the pistons against the cam to cause relative rotation of the cam and rotor, and an internal chamber defined by adjacent portions of the device generally surrounding the portions of the rotor carrying the pistons and portions of the cam engaging the pistons, that improvement wherein:
  • said device includes a fluid drain outlet and ducting extending from said chamber to said fluid drain outlet;
  • control means for regulating flow of fluid in said ducting to maintain the pressure of fluid within said chamber at a pressure level bearing a predetermined relationship to the pressure of fluid within at least one of said fluid inlet and said fluid outlet.
  • controller includes valving within said ducting and responsive to fluid in one of said fluid inlet and said fluid outlet for maintaining the fluid within said chamber at a pressure less than and bearing a predetermined relationship to the pressure of fluid within said one, and override means for maintaining the pressure of the fluid within said chamber at a pressure greater than said pressure within said one.
  • the device of claim 3 including valving responsive to pressure of fluid in each of said main inlet and said main outlet for permitting said fluid flow when said pressure within said intermediate conduit is greater than a pressure bearing a predetermined relationship to the lesser of the pressure within said main inlet and the pressure of fluid within said main outlet.
  • each of said elements is capable of operation as a pump and as a motor.
  • each of said elements comprises a piston engaging said cam and carried by said rotor for movement relative thereto.
  • the device of claim 3 including override means for maintaining the pressure of fluid in said chamber at a level of pressure not less than the pressure of fluid in a selected one of said inlet and said outlet.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Details Of Reciprocating Pumps (AREA)
US65102A 1970-08-19 1970-08-19 Fluid pressure controlling Expired - Lifetime US3662551A (en)

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US6510270A 1970-08-19 1970-08-19

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Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3776102A (en) * 1971-03-03 1973-12-04 Tokico Ltd Variable-displacement type fluid pump or motor
US3815478A (en) * 1970-06-26 1974-06-11 Caterpillar Tractor Co Pipelayer hydraulic drawworks with free-fall
US3854284A (en) * 1971-10-01 1974-12-17 Nutron Corp Engines
US3880052A (en) * 1971-10-01 1975-04-29 Nutron Corp Fluid devices
US4381701A (en) * 1979-09-06 1983-05-03 Regie Nationale Des Usines Renault Servomotor featuring a servovalve controlling a hydraulic drum motor
US20060021341A1 (en) * 2004-08-02 2006-02-02 Thomas Zitterbart Hydraulic system
US20120134848A1 (en) * 2010-11-30 2012-05-31 Nelson Bryan E Hydraulic fan circuit having energy recovery
CN104976169A (zh) * 2014-04-10 2015-10-14 罗伯特·博世有限公司 静液压驱动装置
US20210108623A1 (en) * 2018-03-21 2021-04-15 Dana Motion Systems Italia S.R.L. Bent-axis axial-piston hydraulic machine

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FR3122356B1 (fr) 2021-04-29 2023-03-17 Psa Automobiles Sa Dispositif CALE de train AR fusible en cas de choc AR pour augmenter le rendement de compressibilité de la structure.

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US2617360A (en) * 1945-05-10 1952-11-11 Virgil D Barker Fluid displacement device
US2997962A (en) * 1958-05-08 1961-08-29 Gen Motors Corp Pump
US3435774A (en) * 1966-12-01 1969-04-01 Benton Harbor Eng Works Inc Hydraulic pump or motor
US3433124A (en) * 1967-10-10 1969-03-18 Benton Harbor Eng Works Inc Hydraulic motor
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US3815478A (en) * 1970-06-26 1974-06-11 Caterpillar Tractor Co Pipelayer hydraulic drawworks with free-fall
US3776102A (en) * 1971-03-03 1973-12-04 Tokico Ltd Variable-displacement type fluid pump or motor
US3854284A (en) * 1971-10-01 1974-12-17 Nutron Corp Engines
US3880052A (en) * 1971-10-01 1975-04-29 Nutron Corp Fluid devices
US4381701A (en) * 1979-09-06 1983-05-03 Regie Nationale Des Usines Renault Servomotor featuring a servovalve controlling a hydraulic drum motor
US20060021341A1 (en) * 2004-08-02 2006-02-02 Thomas Zitterbart Hydraulic system
US7320272B2 (en) * 2004-08-02 2008-01-22 Liebherr-Hydraulikbagger Gmbh Hydraulic system
US20120134848A1 (en) * 2010-11-30 2012-05-31 Nelson Bryan E Hydraulic fan circuit having energy recovery
CN104976169A (zh) * 2014-04-10 2015-10-14 罗伯特·博世有限公司 静液压驱动装置
US20150292181A1 (en) * 2014-04-10 2015-10-15 Robert Bosch Gmbh Hydrostatic Drive
US20210108623A1 (en) * 2018-03-21 2021-04-15 Dana Motion Systems Italia S.R.L. Bent-axis axial-piston hydraulic machine

Also Published As

Publication number Publication date
GB1334896A (en) 1973-10-24
SE382243B (sv) 1976-01-19
CA954378A (en) 1974-09-10
DE2137537B2 (de) 1980-12-18
FR2104488A5 (xx) 1972-04-14
BE771255A (fr) 1971-12-16
JPS5610469B1 (xx) 1981-03-07
DE2137537C3 (de) 1981-09-10
DE2137537A1 (de) 1972-02-24

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