US2501165A - Hydrodynamic machine - Google Patents

Hydrodynamic machine Download PDF

Info

Publication number
US2501165A
US2501165A US612252A US61225245A US2501165A US 2501165 A US2501165 A US 2501165A US 612252 A US612252 A US 612252A US 61225245 A US61225245 A US 61225245A US 2501165 A US2501165 A US 2501165A
Authority
US
United States
Prior art keywords
valve
liquid
cylinders
cylinder barrel
pistons
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
US612252A
Inventor
Ferris Walter
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Oilgear Co
Original Assignee
Oilgear Co
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Oilgear Co filed Critical Oilgear Co
Priority to US612252A priority Critical patent/US2501165A/en
Application granted granted Critical
Publication of US2501165A publication Critical patent/US2501165A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • 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
    • F01B1/00—Reciprocating-piston machines or engines characterised by number or relative disposition of cylinders or by being built-up from separate cylinder-crankcase elements
    • F01B1/06—Reciprocating-piston machines or engines characterised by number or relative disposition of cylinders or by being built-up from separate cylinder-crankcase elements with cylinders in star or fan arrangement
    • F01B1/0675—Controlling
    • F01B1/0686—Controlling by changing the effective piston stroke
    • F01B1/0689—Controlling by changing the effective piston stroke by changing the excentricity of one element relative to another element
    • 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
    • F01B13/00—Reciprocating-piston machines or engines with rotating cylinders in order to obtain the reciprocating-piston motion
    • F01B13/04—Reciprocating-piston machines or engines with rotating cylinders in order to obtain the reciprocating-piston motion with more than one cylinder
    • F01B13/06—Reciprocating-piston machines or engines with rotating cylinders in order to obtain the reciprocating-piston motion with more than one cylinder in star arrangement
    • F01B13/061—Reciprocating-piston machines or engines with rotating cylinders in order to obtain the reciprocating-piston motion with more than one cylinder in star arrangement the connection of the pistons with the actuated or actuating element being at the outer ends of the cylinders
    • F01B13/063—Reciprocating-piston machines or engines with rotating cylinders in order to obtain the reciprocating-piston motion with more than one cylinder in star arrangement the connection of the pistons with the actuated or actuating element being at the outer ends of the cylinders with two or more series radial piston-cylinder units
    • F01B13/065—Reciprocating-piston machines or engines with rotating cylinders in order to obtain the reciprocating-piston motion with more than one cylinder in star arrangement the connection of the pistons with the actuated or actuating element being at the outer ends of the cylinders with two or more series radial piston-cylinder units directly located side by side
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
    • F03C1/00—Reciprocating-piston liquid engines
    • F03C1/02—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders
    • F03C1/04—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinders in star or fan arrangement
    • F03C1/0403—Details, component parts specially adapted of such engines
    • F03C1/0435—Particularities relating to the distribution members
    • F03C1/0444—Particularities relating to the distribution members to plate-like distribution members

Definitions

  • This invention relates to hydrodynamic machines of the type which will function as pumps when driven mechanically and will function as hydraulic motors when supplied with liquid under pressure.
  • the machine to which the invention relates in particular has its pistons and cylinders arranged in a rotatable cylinder barrel, a valve seat arranged upon an end of the cylinder barrel, and a flat valve engaging the seat to control the flow of motive liquid to and from the cylinders.
  • the motive liquid which is ordinarily oil, forms a lubricating film between the valve and its seat and the pressure in the valve and in the film tends to move the valve away from its seat but is prevented from doing so by a plurality of hold-up motors which are energized by the motive liquid and each of which ordinarily includes a stationary cylinder and a piston fitted in the cylinder.
  • the hold-up pistons remain stationary for long intervals of time and never move more than the very slight amount necessary to compensate for varying deflections in the supporting structure and variations in the thickness of the lubricating film caused by variations in the viscosity of the liquid clue to variations in temperature.
  • Hydrodynamic machines of this type are in extensive use and operate successfully if the motive liquid is relatively clean but after an extended period of use the motive liquid often becomes contaminated with particles of solid and semisolid matter some of which lodge between the pistons and the cylinder walls of hold-up motors. Since the hold-up pistons have such limited movements, they are unable to eject the particles of matter from between their outer walls and the walls of their cylinders with the result that the particles accumulate therein until they cause the hold-up pistons to stick in their cylinders, thereby impairing the efliclency of the machine and sometimes rendering it inoperative until the hold-up pistons are removed and cleaned.
  • the present invention has as an object to provide a hydrodynamic machine in which the danger of the hold-up pistons sticking in their cylinders is substantially eliminated.
  • the motor of a hydraulic transmission should start under load simultaneously with the operation of the element which controls the flow of liquid thereto but, when a pump is adjusted from zero displacement to a positive displacement, it must com-press the liquid in the motor and in the eon- 2 necting channels-before the motor can start to operate.
  • Another object of the present invention is to provide a pump which when at zero displacement will create rapid intermittent pulsations of pressure and thereby enable a motor connected thereto to start substantially simultaneously with the adjustment of the pump to a positive displacement.
  • Fig. l is a transverse section through a hydrodynamic machine in which the invention is embodied, the section being taken on the line II of Fig. 2.
  • Fig. 2 is in part a longitudinal section taken on the irregular line 2--2 of Fig. 1 and in part a circuit diagram showing the machine connected to a hydraulic motor.
  • Fig. 3 is a transverse section taken on the irregular line 3-3 of Fig. 2.
  • Fig. 4 is a transverse section through a distributing block through which liquid flows to and from the cylinder barrel, the view being taken in the plane of the line 44 of Fig. 2.
  • Fig. 5 is a section through the distributing block and the adjacent valve, the section being taken on the line 55 of Fig. 4.
  • Fig. 6 is a diagram illustrating a modification of the arrangement shown in Fig. 2.
  • the pump has its mechanism arranged within and carried by a casing l which consists of a plurality of parts and in practice has a plurality of passages formed therein but, in order to simplify the drawings, only fragments of the casing have been shown and certain of the passages have been represented by external channels.
  • Cylinder barrel 4 has a plurality of cylinders formed therein and shown arranged in two circular rows, each cylinder in one row being indicated by the reference numeral 6 and each cylinder in the other row being indicated by the reference numeral 6*.
  • Each cylinder 8 has a piston 1 fitted therein and its inner end connected to a passage 8 which is formed in cylinder barrel 4 and extends through the left end thereof.
  • Each cylinder 6 has a piston l fitted therein and it has its inner end connected to a passage 8 which is formed in cylinder barrel 4 and extends through the right end thereof.
  • the cylinders have been shown as being radial and the pistons have been shown as having the outer ends or heads thereof in contact with conical reaction surfaces 9 and 9* arranged upon the inside of an annular thrust member l which extends around cylinder barrel 4, the outer end of each piston being so shaped that the reaction surface makes contact therewith upon a single spot which is offset far enoughfrom the piston axis to cause the piston to rotate in its cylinder as it is reciprocated therein during rotation of cylinder barrel 4 and thrust member l0 as fully explained in Patent No. 2,074,068.
  • the volumetric capacity of the pump may be increased by increasing the number of rows of cylinders, or it may be increased by increasing the number of cylinders in each row and inclining alternate cylinders in each row in opposite directions and having the outer ends of the pistons in contact with a circular reaction surface as shown in Patent No. 2,406,138. If the pump is to operate at a high pressure, such as 2500 p. s. i., the pistons are reduced in diameter and provided on their outer ends with enlarged heads as shown in Patent No. 2,074,068.
  • Thrust member ID is rotatably supported as by means of a roller bearing ll. placement pump or motor, thrust member [0 is adapted to rotate upon a stationary axis but it has been shown supported by bearing H within a displacement varying member or slide block l2 which is slidably supported within casing I as by means of two roller bearings l3 and I4 so that when functioning as a pump it will deliver liquid in a direction and at a rate dependent upon the direction and the distance that the axis of slide block I2 is offset from the axis of cylinder barrel 4.
  • Slide block l2 may be shifted in response to operation of a suitable control such as the control illustrated and described in Patent No. 2,406,138.
  • slide block I2 is constantly urged toward the right by a servomotor l which engages the left side thereof and includes a spring IS.
  • a roller I! carried by slide block I 2 at the right side thereof is urged by servo-motor l5 against the face of a cam l8 which is guided by a roller hearing I 9 and has its ends connected to pistons 20 and 2
  • Cylinder 22 is continuously supplied with liquid at a substantially constant pressure and cylinder 23 is larger than cylinder 22 so that, when it is supplied with liquid at the same pressure,
  • cylinder barrel 4 has been shown as having its ends recessed and valves 24 and 24- extending into the recesses.
  • Prior pumps of the fiat valve type have a valve seat formed directly upon the recessed end of the cylinder barrel and arranged parallel to the plane of rotation of the cylinder barrel but in the present invention the valve seat is inclined to the plane of rotation to cause the flat valve to wabble during rotation of the cylinder barrel for reasons to be presently explained.
  • Inclined valve seats may be formed directly upon opposite ends of cylinder barrel 4 but preferably two inclined valve seats 26 and 26" are formed. respectively, upon the outer faces of two beveled wear plates 2'! and 21- which are arranged upon opposite ends of cylinder barrel 4 and fixed for rotation therewith.
  • Wear plate 21 has extending therethrough a plurality of cylinder ports 28 each of which registers with a passage 8
  • wear plate 21 has extending therethrough a plurality of cylinder ports 28 each of which registers with a passage 8.
  • Valve 24 is provided at its center with an opening 29 which is larger than shaft 2 so that, during rotation of cylinder barrel 4, valve 24 may wabble without engaging shaft 2.
  • the inner end or face of valve 24 has formed therein two diametrically opposed. substantially crescent shaped ports 3
  • Valve 24 may be supported and prevented from rotating in any suitab e manner. As shown, two pins 31 are fixed in distributing block 25 at opposite sides of shaft 2 and extend, respectively. into two sockets 38 formed in valve 24. Pins 31 fit loosely in sockets 38 to permit valve 24 to wabble while preventing any substantial rotation or radial movement thereof.
  • liquid in one port of valve 24 is under a high pressure
  • the liquid in the other port of valve 24 is under a low, zero or negative pressure
  • minute quantities of liquid will escape from the high pressure port and spread over valve seat 26 and the face of valve 24 to form a lubricating film therebetween.
  • the pressure prevailing in the high pressure port will extend into the lubricating film and the pressure prevailing in one or both ports and in the film will tend to move the valve away from its seat 26.
  • the film pressure varies from a high pressure at the edge of the high pressure port to a low or zero pressure at the edge of the other port and to zero at the edges of the valve seat. Consequently, the center of pressure is not on the center of the valve but, if the pressure in the low pressure port is zero or negative, the center of pressure is near the center of a high pressure area which extends around the high pressure port or, if there is pressure in the low pressure port, there will be one center of pressure near the center of the high pressure area which extends around the high pressure port and another center of pressure near the center of a low pressure area which extends around the low pressure port.
  • the force exerted by the liquid in the low pressure area is ordinarily so small that it may be disregarded in the present explanation and only the high pres"ure area considered, it being understood that the center of high pressure is on one side of the cylinder barrel axis when one port is the high pressure port and on the other side of the cylinder barrel axis when the other port is the high pressure port.
  • the pressure area may be considered as being equal to the area of the high pressure port plus one half the valve face area across which the liquid passes.
  • This pressure area will be referred to herein as the blow-off area.
  • the force which tends to move the valve away from its seat. hereinafter referred to as the "blow-off force. is determined by multiplying the blow-off area by the unit working pressure.
  • the cylinder barrel is always provided with an odd number of cylinder ports so that an odd number of cylinder ports and an even number of cylinder ports communicate alternately with the high pressure valve port during rotation of the cylinder barrel. For example, if each end of cylinder barrel 4 is provided with seven cylinder ports 28 as shown, three cylinder ports 28 will communicate with the high pressure port during a part of a revolution of cylinder barrel 4 and four cylinder ports 28 will communicate with the same valve port during the preceding and succeeding parts of the revolution.
  • blow-off area will vary as the cylinder ports move into and out of communication with the high pressure valve port, and the center of the blow-off force will shift both radially and circumferentially but it is always near the vertical center line of the valve and is always spaced a short distance radially inward from the inner edge of the high pressure valve port.
  • blow-oil force could be opposed by a single hold-up motor arranged within distributing block and engaging valve 24 upon its vertical center line a short distance inward from the inner edge of the high pressure valve port but in that location it would occupy a part of the space required by shaft 2. Therefore, the blow-01f force is opposed by two spaced apart hold-up motors which are arranged in distributing block 25 and engage valve 24 at equal distances from the vertical center line.
  • the two hold-up motors are the equivalent of and function in the same manner as a single hold-up motor arranged upon the vertical center line of the valve.
  • are arranged in distributing block 25 above its horizontal center line and two hold-up motors 42 and 43 are arranged in distributing block 26 below its horizontal center line. All four hold-up motors are equidistant from the horizontal center line and are equidistant from the vertical center line. Also, auxiliary hold-up motors are ordinarily provided to compensate for variations in the blow-off area as explained in Patent No. 2,484,337 but such auxiliary motors have been omitted from the drawings to avoid complicating the views.
  • the four hold-up motors are identical and each has a hollow piston 44 fitted in a cylinder 45 which is formed in distributing block 25.
  • Each piston 44 is urged by a spring 46 against an annular sealing member 41 which is urged by spring 46 against the outer end of valve 24, the contacting surfaces of member 41 and valve 24 being ground fiat and the contacting surfaces of piston 44 and member 41 being ground spherical to provide self-aligning liquid tight seals therebetween.
  • communicate through passages 35 and chamber 33 with port 3 in valve 24 and the openings through the pistons 44 and sealing members 41 of motors 42 and 43 communicate through passages 36 and chamber 34 with port 32 in valve 24.
  • are connected by a passage 48 (Fig. 4) to each other and to a passage 49 which extends outward through distributing block 25 for connection to one side of an external circuit.
  • the cylinders 45 of motors 42 and 43 are connected by a passage 50 to each other and to a passage 5
  • valve 24 is urged against its seat 26 by the constant force supnlied'by the four springs 44 and by a force which varies in accordance with variations in the pressure of the motive liquid.
  • Valve 24 is identical to valve 24 and distributing block 25'- is identical to distributing block 25. Consequently, they have not been fully illustrated and a description thereof is deemed unnecessary, like parts and passages as far as shown being indicated by like reference numerals with the exponent a added to the reference numerals applied to valve 24- and distributing block 25.
  • Passage 49 in block 25 and passage 49 in block 25 are connected to each other by a channel 52.
  • in block 25'- are connected to each other icy a channel 53.
  • Channels 52 and 53 have been shown as external channels and as being connected, respectively, by channels 54and 55 to opposite ends of a. hydraulic motor 56 but in practice they may be formed in the casing of the machine and connected to a different device.
  • Passages 8 and 8 are equally spaced in the cylinder barrel 4 and valves 24 and 24"- are symmetrical about their horizontal center lines so that, when cylinder barrel 4 is rotated, the mahin will fu ction as a pump and will deliver liquid in a direction and at a rate. dependent upon the direction and rate of rotation of cylinder barrel 4 and upon the direction and distance slide block I2 is ofiset from its neutral position, it being understood that, when slide block I2 is in its neutral position so that thrust member III is concentric with cylinder barrel 4, pistons I and 1' will not be reciprocated and no liquid will be delivered by the pump.
  • valves 24 and 24' The inward moving pistons will eject liquid from their cylinders through passages 8 and 3* connected thereto, the upper parts of valves 24 and 24', the upper parts of distributing blocks 25 and 25', channel 52 and channel 54 to the external circuit and the resistance encountered by the liquid in the external circuit will cause pressure to rise and act upon the pistons 44 of motors 46, 4
  • valves 24 and 24 During rotation of cylinder barrel 4, inclined valve seats 26 and 26 cause valves 24 and 24 to wabble and continuously reciprocate pistons 44 which are thus enabled to dislodge particles of matter which tend to accumulate between the walls of cylinders and pistons, thereby reducing to a minimum all danger of the hold-up pistons sticking in their cylinders.
  • Each piston 44 alternately draws liquid into and ejects liquid from its cylinder as it reciprocates therein. That is, pistons 44 pump liquid so that limited volumes of liquid are alternately subtracted from and added to the liquid dise charged from pump cylinders 6 and 6 and also the liquid supplied to pump cylinders 6 and 6.
  • valve seats 25 and 26 are inclined in the same direction as shown in Fig. 2, each piston 44 at one end of the pump will draw liquid into its cylinder 45 at the same time and at the same rate that the corresponding piston 44 at the other end of the pump ejects liquid from its cylinder 45. Consquently, there will be no flow from hold-up cylinders 45 to an external circuit so that, if the pump were connected as shown in Fig. 2, piston 51 of motor 56 would be moved at a uniform rate when the pump had a positive displacement and it would remain stationary when the pump was at zero displacement.
  • Substantially instantaneous starting of the motor in response to adjustment of the pump to a positive displacement in either direction, or to reversal of pump discharge by moving the slide block across neutral position, may be effected by inclining the pump valve seats 26 and 26 in opposite directions as shown in Fig. 6. With the valve seats inclined in opposite directions, rotation of cylinder barrel 4 will cause corresponding pistons 44 at opposite ends of the pump to be moved alternately toward and from each other.
  • pistons I and 1 wil When the pump is ajusted to zero displacement and cylinder barrel 4 is rotated, pistons I and 1 wil not be reciprocated and no liquid will be discharged thereby but hold-up pistons 44 will be reciprocated in their cylinders.
  • the outward moving pistons 44 will expel liquid from their cylinders into one side of the hydraulic circuit and the cylinders containing the inward moving pistons will be filled with liquid from the other side of the circuit.
  • Patent No. 2,406,138 and in PatentNo. 2,484,337 In this case, there will be no actual flow in the circuit.
  • the pump is connected into a closed bydraulic circuit with a reciprocating hydraulic motor as shown in Fig. 6 and the parts are so proportioned that the volume of liquid discharged by the outward moving pistons 44 into one side of the circuit is sufficient to compress the liquid therein and to cause the piston 51 of the motor to move slightly, the cylinders containing the inward moving pistons 44 will be filled with liquid by the expansion of the liquid in the other side of the circuit and by the liquid expelled by piston 51 from the motor cylinder. In this case there will be a slig t flow of liquid in opposite directions alternately and piston 51 will be vibrated rapidly, making one complete reciprocation during each revolution of cylinder barel 4.
  • the motor will start at the same instant but, if at that instant the outward moving pistons 44 are creating pressure in the opposite side of the circuit, the motor will start as soon as cylinder barrel 4 has made one-- half or less of a revolution which in the above example would be of a second or less and that arranged upon each of the two opposite ends thereof and inclined to the plane of rotation thereof and passages extending from some of said cylinders through one of said valve seats and other passages extending from the other of said cylinders through the other of said valve seats, two flat valves engaging said seats respectively to control the flow of liquid to and from said cylinders, each of said valves having inlet and outlet ports with which each of said passages registers alternately during rotation of said cylinder barrel, hold-up motors for urging said valves against said seats and each including a piston and a cylinder, means providing reactances for said hold-up motors
  • a rotatable cylinder barrel having pistons and cylinders arranged therein, a valve seat arranged upon an end thereof and inclined to the plane of rotation thereof and passages extending from said cylinders through said valve seat, a flat valve engaging said seat to control the now of liquid to and from said cylinders, hold-up motors for urging said valve against said seat and each including a piston and a cylinder, and means providing a reactance for said hold-up motors the inclined valve seat causing said valve duringrotation of said cylinder barrel to wabble and effect relative reciprocation of said hold-up motor pistons and cylinders.
  • a rotatable cylinder barrel having pistons and cylinders arranged therein, a beveled wear plate fixed upon an end thereof and providing a valve seat which is inclined to the plane of rotation thereof and passages extending from said cylinders through said valve seat, a flat valve engaging said seat to control the flow of liquid to and from said cylinders, hold-up motors for urging said valve against said seat and each including a piston and a cylinder, and means providing a reactance for said hold-up motors, the inclined valve seat causing said valve during rotation of said cylinder barrel to wabble and effect relative reciprocation of said hold-up motor pistons and cylinders.
  • a rotatable cylinder barrel having pistons and cylinders arranged therein, a valve seat said valve seats and other passages extending from the other of said cylinders through the other of said valve seats, two flat valves engaging said seats respectively to control the flow of liquid to and from said cylinders, each of said valves having inlet and outlet ports with which each of said passages registers alternately during rotation of said cylinder barrel, hold-up motors for urging said valves against said seats and each including a piston and a cylinder, means providing reactances for said hold-up motors, the inclined valve seats causing said valves during rotation of said cylinder barrel to wabble and effect relative reciprocation of said hold-up motor pistons and cylinders, means for connecting said inlet ports to each other and to an external circuit, and means for connecting said outlet ports to each other and to an external circuit.
  • a rotatable cylinder barrel having pistons and cylinders arranged therein, a valve seat arranged upon an end thereof and inclined to the plane of rotation thereof and passages extending from said cylinders through said valve seat, a fiat valve engaging said seat to control the flow of liquid to and from said cylinders and provided with inlet and outlet ports in the inner face thereof and with passages extending through the outer face thereof into communication with said ports, a stationary distributing block spaced from the outer face of said valve, and hold-up motors arranged in said block in alignment with said passages, each hold-up motor, including a cylinder having a connection for the flow of liquid to and from an external circuit, a hollow piston fitted in said cylinder and a hollow sealing member arranged between said piston and the outer face of said valve so that liquid flows through said hold-up motors to and from said cylinder barrel and any pressure in said liquid causes said pistons to urge said valve against said valve seat, said inclined valve seat during rotation of said cylinder barrel causing said
  • a rotatable cylinder barrel having pistons and cylinders arranged therein, a beveled wear plate fixed upon an end thereof and providing a valve seat which is inclined to the plane of rotation thereof and passages extending from said cylinders through said seat, a flat valve engaging said seat to control the flow of liquid to and from said cylinders and provided with inlet and outlet ports in the inner face thereof and with passages extending through the outer face thereof into communication with said ports, a stationary distributing block spaced from the outer face of said valve, and hold-up motors arranged in said block in alignment with said passages, each hold-up motor including a cylinder having a connection for the fiow of liquid to and from an external circuit, a hollow piston fitted in said cylinder and a hollow sealing member arranged between said piston and the outer face of said valve so that liquid flows through said hold-up motors to and from said cylinder barrel and any pressure in said liquid causes said pistons to urge said valve against said valve seat, said inclined valve seat during rotation of
  • a rotatable cylinder barrel having a plurality of pistons and cylinders arranged therein, a valve seat arranged upon each of the two ends thereof and inclined to the plane of rotation thereof, passages leading from a part of said cylinders through one of said valve seats and other passages leading from the other cylinders through the other of said valve seats, two flat valves arranged at opposite ends of said cylinder barrel and engaging said seats to control the flow of liquid to and from,said cylinders and provided with inlet and outlet ports in the inner faces thereof and with passages extending through the outer faces thereof into communication with said ports, a stationary distributing block spaced from the outer face of each valve, and hold-up motors arranged in said blocks in alignment with said valve passages, each holdup motor including a cylinder having a connection for the flow of liquid to and from an external circuit, a hollow piston fitted in said cylinder and a hollow sealing member arranged between said piston and the outer face of the adjacent valve so that liquid flows through said hold-
  • each hold-up motor including a cylinder having a connection for the flow of liquid to and from an external circuit, a hollow piston fitted in said cylinder and a hollow sealing member arranged between said piston and the outer face of said valve so that liquid flows through said hold-up motors to and from said cylinder barrel and any pressure in said liquid causes said pistons to urge said valves against said valve seat and said inclined valve seats during rotation of
  • a hydraulic transmission comprising a motor, fluid channels, and a pump connected to said motor by said channels to form therewith a hydraulic circuit and including a rotatable cylinder barrel having a plurality of pistons and cylinders arranged therein, the combination of a valve seat arranged upon each end of said cylinder barrel and inclined to the plane of rotation thereof, said cylinder barrel having passages leading from some of said cylinders through one of said valve seats and other passages leading from the other of said cylinders through the other valve seat, two flat valves arranged at opposite ends of said cylinder barrel and engaging said seats to control the flow of liquid to and from said cylinders and provided withinlet and outlet ports in the inner faces thereof and with passages extending through the outer faces thereof into communication with said ports, a stationary distributing block spaced from the outer face of each valve, and hold-up motors arranged in said blocks in alinement with said valve passages, each hold-up motor including a cylinder having a connection for the flow of liquid to and from said circuit, a hollow piston fitted in
  • a hydraulic transmission comprising a motor, fluid channels, and a pump connected to said motor by said channels to form therewith a hydraulic circuit and including a rotatable cylinder barrel having a plurality of pistons and cylinders arranged therein.
  • a beveled wear plate fixed upon each end of said cylinder barrel and providing a valve seat which is inclined to the plane of rotation of said cylinder barrel, said cylinder barrel having passages leading from some of said cylinders through one of said valve seats and other passages leading from the other of said cylinders through the other valve seat, two flat valves arranged at opposite ends of said cylinder barrel and engaging said seats to control the flow of liquid to and from said cylinders and provided with inlet and outlet ports in the inner faces thereof and with passages extending through the outer faces thereof into communication with said ports, a stationary distributing block spaced from the outer face of each valve, and hold-up motors arranged in said blocks in alinement with said valve passages, each hold-up motor including a cylinder having aconnection for the flow
  • a hydraulic transmission comprising a motor, fluid channels, and a pump connected to said motor by said channels to form therewith a hydraulic circuit and including a rotatable cylinder barrel having a plurality of pistons and cylinders arranged therein, the combination of a valve seat arranged-upon each end of said cylinder barrel and inclined to the plane of rotation thereof, said cylinder barrel having passages leading from some of said cylinders through one of said valve seats and other passages leading from the other of said cylinders through the other valve seat, two fiat valves arranged at opposite ends of said cylinder barrel and engaging said seats to control the flow of liquid to and from said cylinders and provided with inlet and outlet ports in the inner faces thereof and with passages extending through the outer faces thereof into communication with said ports, a stationary distributing block spaced from the outer face of each valve.
  • each hold-up motor including a cylinder having a connection for the flow of liquid to and from an external circuit, a hollow piston fitted in said cylinder and a hollow sealing member arranged between said piston and the outer face of the adjacent valve so that liquid flows through said hold-up motors to and from said cylinder barrel and any pressure in said liquid causes said pistons to urge said valves against said valve seats, said inclined valve seats during rotation of said cylinder barrel causing said valves to wabble and reciprocate said holdup pistons to prevent them from sticking in their cylinders and to cause each hold-up piston during reciprocation thereof to function as a pump and alternately increase and decrease the flow of liquid therethrough by a limited amount, and said valve seats being inclined in the same direction to cause corresponding hold-up pistons at opposite ends of said cylinder barrel to pump in opposite phase and thereby neutralize the pumping effects of each other so that the flow of liquid to said motor is unaffected by reciprocation of said hold-up pistons.
  • a hydraulic transmission comprising a motor, fluid channels, and a pump connected to said motor by said channels to form therewith a hydraulic circuit and including a rotatable cylinder barrel having a plurality of pistons and cylinders arranged therein, the combination of a beveled wear plate fixed upon each end of said cylinder barrel and providing a valve seat which is inclined to the plane of rotation of said cylinder barrel, said cylinder barrel having passages leading from some of said cylinders through one of said valve seats and other passages leading from the other of said cylinders through the other valve seat, two flat valves arranged at opposite ends of said cylinder barrel and engaging said seats to control the flow of liquid to and from said cylinders and provided with inlet and outlet ports in the inner faces thereof and with passages extending through the outer faces thereof into communication with said ports, a stationary distributing block spaced from the outer faces of each valve, and hold-up motors arranged in said blocks in alinement with said valve passages, each hold-up motor including a cylinder having a connection for the flow

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Details Of Reciprocating Pumps (AREA)
  • Reciprocating Pumps (AREA)

Description

MQJJLB 21, 1950 w. FERRIS 2,501,165
HYDRODYNAMIC MACHINE Filed Aug. 23, 1945 4 Sheets-Sheet l JNVENTOR. WALTER .FERRIS ATTDRNEV March 211 1950 w, FERRls 2,501,165
HYDRODYNAMIC MACHINE Filed Aug. 23,. 1945- 4 Sheets-Sheet 2 INVENTOR.
- ALTER FERRES f ATTGRNEEV Mamh 21, 31950 w. FERRIS 5 9 HYDRODYNAMIC MACHINE Filed Aug. 23, 1945 r Sheets-Sheet 3 INVENTOR. WALTER FERRES LW'TORNEY March 231 1950 w. FERRIS HYDRODYNAMIC MACHINE Filed Aug. 23, 1945 4 Sheets-Sheet 4 FERRIS m m V a E T L A ATTORNEY Patented Mar. 21, 1950 UNITED STATES PATENT OFFICE HYDBODYNAMIC MACHINE Walter Ferris, Milwaukee, wis assignor to The Oilgear Company, Milwaukee, Wis., a corporation of Wisconsin 12 Claims.
This invention relates to hydrodynamic machines of the type which will function as pumps when driven mechanically and will function as hydraulic motors when supplied with liquid under pressure. The machine to which the invention relates in particular has its pistons and cylinders arranged in a rotatable cylinder barrel, a valve seat arranged upon an end of the cylinder barrel, and a flat valve engaging the seat to control the flow of motive liquid to and from the cylinders.
The motive liquid, which is ordinarily oil, forms a lubricating film between the valve and its seat and the pressure in the valve and in the film tends to move the valve away from its seat but is prevented from doing so by a plurality of hold-up motors which are energized by the motive liquid and each of which ordinarily includes a stationary cylinder and a piston fitted in the cylinder. The hold-up pistons remain stationary for long intervals of time and never move more than the very slight amount necessary to compensate for varying deflections in the supporting structure and variations in the thickness of the lubricating film caused by variations in the viscosity of the liquid clue to variations in temperature.
Hydrodynamic machines of this type are in extensive use and operate successfully if the motive liquid is relatively clean but after an extended period of use the motive liquid often becomes contaminated with particles of solid and semisolid matter some of which lodge between the pistons and the cylinder walls of hold-up motors. Since the hold-up pistons have such limited movements, they are unable to eject the particles of matter from between their outer walls and the walls of their cylinders with the result that the particles accumulate therein until they cause the hold-up pistons to stick in their cylinders, thereby impairing the efliclency of the machine and sometimes rendering it inoperative until the hold-up pistons are removed and cleaned.
The present invention has as an object to provide a hydrodynamic machine in which the danger of the hold-up pistons sticking in their cylinders is substantially eliminated.
In certain situations it is desirable that the motor of a hydraulic transmission should start under load simultaneously with the operation of the element which controls the flow of liquid thereto but, when a pump is adjusted from zero displacement to a positive displacement, it must com-press the liquid in the motor and in the eon- 2 necting channels-before the motor can start to operate.
Another object of the present invention is to provide a pump which when at zero displacement will create rapid intermittent pulsations of pressure and thereby enable a motor connected thereto to start substantially simultaneously with the adjustment of the pump to a positive displacement.
These and other objects and advantages will be apparent from the following description of an embodiment of the invention shown somewhat diagrammatically in the accompanying drawing in which the views are as follows:
Fig. l is a transverse section through a hydrodynamic machine in which the invention is embodied, the section being taken on the line II of Fig. 2.
Fig. 2 is in part a longitudinal section taken on the irregular line 2--2 of Fig. 1 and in part a circuit diagram showing the machine connected to a hydraulic motor.
Fig. 3 is a transverse section taken on the irregular line 3-3 of Fig. 2.
Fig. 4 is a transverse section through a distributing block through which liquid flows to and from the cylinder barrel, the view being taken in the plane of the line 44 of Fig. 2.
Fig. 5 is a section through the distributing block and the adjacent valve, the section being taken on the line 55 of Fig. 4.
Fig. 6 is a diagram illustrating a modification of the arrangement shown in Fig. 2.
The machine chosen for illustration is of the type illustrated and described in application Serial No. 485,279 filed May 1, 1943, now Patent No. 2,484,337, to which reference may be had for details of construction not fully illustrated herein. This machine will function either as a pump or as a motor but, in order to simplify the description, it will be referred to herein as a pump. It is to be understood however that the invention is equally applicable to a motor and that the invention is in no way limited to a pump nor to a pump having fiat valves at both ends of its cylinder barrel.
As shown, the pump has its mechanism arranged within and carried by a casing l which consists of a plurality of parts and in practice has a plurality of passages formed therein but, in order to simplify the drawings, only fragments of the casing have been shown and certain of the passages have been represented by external channels.
Power is transmitted to the pump through a shaft 2 which is journaled in a bearing 3 carried by casing I. Shaft 2 has its inner end splined or otherwise suitably connected to a cylinder barrel 4 which is rotatably supported within casing I by bearings 5 and 5 carried thereby. Cylinder barrel 4 has a plurality of cylinders formed therein and shown arranged in two circular rows, each cylinder in one row being indicated by the reference numeral 6 and each cylinder in the other row being indicated by the reference numeral 6*. Each cylinder 8 has a piston 1 fitted therein and its inner end connected to a passage 8 which is formed in cylinder barrel 4 and extends through the left end thereof. Each cylinder 6 has a piston l fitted therein and it has its inner end connected to a passage 8 which is formed in cylinder barrel 4 and extends through the right end thereof.
The cylinders have been shown as being radial and the pistons have been shown as having the outer ends or heads thereof in contact with conical reaction surfaces 9 and 9* arranged upon the inside of an annular thrust member l which extends around cylinder barrel 4, the outer end of each piston being so shaped that the reaction surface makes contact therewith upon a single spot which is offset far enoughfrom the piston axis to cause the piston to rotate in its cylinder as it is reciprocated therein during rotation of cylinder barrel 4 and thrust member l0 as fully explained in Patent No. 2,074,068.
The volumetric capacity of the pump may be increased by increasing the number of rows of cylinders, or it may be increased by increasing the number of cylinders in each row and inclining alternate cylinders in each row in opposite directions and having the outer ends of the pistons in contact with a circular reaction surface as shown in Patent No. 2,406,138. If the pump is to operate at a high pressure, such as 2500 p. s. i., the pistons are reduced in diameter and provided on their outer ends with enlarged heads as shown in Patent No. 2,074,068.
Thrust member ID is rotatably supported as by means of a roller bearing ll. placement pump or motor, thrust member [0 is adapted to rotate upon a stationary axis but it has been shown supported by bearing H within a displacement varying member or slide block l2 which is slidably supported within casing I as by means of two roller bearings l3 and I4 so that when functioning as a pump it will deliver liquid in a direction and at a rate dependent upon the direction and the distance that the axis of slide block I2 is offset from the axis of cylinder barrel 4.
Slide block l2 may be shifted in response to operation of a suitable control such as the control illustrated and described in Patent No. 2,406,138. As shown in Fig. 1, slide block I2 is constantly urged toward the right by a servomotor l which engages the left side thereof and includes a spring IS. A roller I! carried by slide block I 2 at the right side thereof is urged by servo-motor l5 against the face of a cam l8 which is guided by a roller hearing I 9 and has its ends connected to pistons 20 and 2| fitted, respectively, in cylinders 22 and 23 carried by casing I, roller bearing l9 preventing cam l8 from being deflected by the thrust of servo-motor l5.
Cylinder 22 is continuously supplied with liquid at a substantially constant pressure and cylinder 23 is larger than cylinder 22 so that, when it is supplied with liquid at the same pressure,
In a constant dispiston 2 I' will move cam l8 downward and permit servo-motor to move slide block l2 toward the right and, when cylinder 23 is opened to drain, piston will move cam l8 upward and cause it to move slide block l2 toward the left.
The flow of liquid to and from cylinders 6 and 6' is controlled by two fiat valves 24 and 24 which are arranged, respectively, between opposite ends of cylinder barrel 4 and two identical distributing blocks 25 and 25 which are fixed to or formed integral with casing I. In order to maintain the overall length of th pump at a minimum, cylinder barrel 4 has been shown as having its ends recessed and valves 24 and 24- extending into the recesses.
Prior pumps of the fiat valve type have a valve seat formed directly upon the recessed end of the cylinder barrel and arranged parallel to the plane of rotation of the cylinder barrel but in the present invention the valve seat is inclined to the plane of rotation to cause the flat valve to wabble during rotation of the cylinder barrel for reasons to be presently explained.
Inclined valve seats may be formed directly upon opposite ends of cylinder barrel 4 but preferably two inclined valve seats 26 and 26" are formed. respectively, upon the outer faces of two beveled wear plates 2'! and 21- which are arranged upon opposite ends of cylinder barrel 4 and fixed for rotation therewith. Wear plate 21 has extending therethrough a plurality of cylinder ports 28 each of which registers with a passage 8, and wear plate 21 has extending therethrough a plurality of cylinder ports 28 each of which registers with a passage 8.
Valve 24 is provided at its center with an opening 29 which is larger than shaft 2 so that, during rotation of cylinder barrel 4, valve 24 may wabble without engaging shaft 2. The inner end or face of valve 24 has formed therein two diametrically opposed. substantially crescent shaped ports 3| and 32 (Figs. 2 and 3) with which each cylinder port 8 communicates alternately as cylinder barrel 4 rotates. Ports 3| and 32 communicate, respectively, with two chambers 33 and 34 (Figs. 2 and 5) which are formed within valve 24 and have passages 35 and 36 leading therefrom respectively through the outer end of the valve.
Valve 24 may be supported and prevented from rotating in any suitab e manner. As shown, two pins 31 are fixed in distributing block 25 at opposite sides of shaft 2 and extend, respectively. into two sockets 38 formed in valve 24. Pins 31 fit loosely in sockets 38 to permit valve 24 to wabble while preventing any substantial rotation or radial movement thereof.
When the machine is performing work either as a pump or as a motor, liquid in one port of valve 24 is under a high pressure, the liquid in the other port of valve 24 is under a low, zero or negative pressure, and minute quantities of liquid will escape from the high pressure port and spread over valve seat 26 and the face of valve 24 to form a lubricating film therebetween. The pressure prevailing in the high pressure port will extend into the lubricating film and the pressure prevailing in one or both ports and in the film will tend to move the valve away from its seat 26.
Due to the pressure being very high in one valve port and very low or absent in the other valve port, the film pressure varies from a high pressure at the edge of the high pressure port to a low or zero pressure at the edge of the other port and to zero at the edges of the valve seat. Consequently, the center of pressure is not on the center of the valve but, if the pressure in the low pressure port is zero or negative, the center of pressure is near the center of a high pressure area which extends around the high pressure port or, if there is pressure in the low pressure port, there will be one center of pressure near the center of the high pressure area which extends around the high pressure port and another center of pressure near the center of a low pressure area which extends around the low pressure port.
However, the force exerted by the liquid in the low pressure area is ordinarily so small that it may be disregarded in the present explanation and only the high pres"ure area considered, it being understood that the center of high pressure is on one side of the cylinder barrel axis when one port is the high pressure port and on the other side of the cylinder barrel axis when the other port is the high pressure port.
Since an area of the valve equal to the area of the high pressure port is under full working pressure and since a film of liquid leaks from the high pressure port to the nearest low pressure areas so that the film is under full working pressure at the edges of the high pressure port and has low or zero pressure at the edges of the nearest low pressure area, the pressure area may be considered as being equal to the area of the high pressure port plus one half the valve face area across which the liquid passes. This pressure area will be referred to herein as the blow-off area. The force which tends to move the valve away from its seat. hereinafter referred to as the "blow-off force. is determined by multiplying the blow-off area by the unit working pressure.
The cylinder barrel is always provided with an odd number of cylinder ports so that an odd number of cylinder ports and an even number of cylinder ports communicate alternately with the high pressure valve port during rotation of the cylinder barrel. For example, if each end of cylinder barrel 4 is provided with seven cylinder ports 28 as shown, three cylinder ports 28 will communicate with the high pressure port during a part of a revolution of cylinder barrel 4 and four cylinder ports 28 will communicate with the same valve port during the preceding and succeeding parts of the revolution. Consequently, the blow-off area will vary as the cylinder ports move into and out of communication with the high pressure valve port, and the center of the blow-off force will shift both radially and circumferentially but it is always near the vertical center line of the valve and is always spaced a short distance radially inward from the inner edge of the high pressure valve port.
If shaft 2 did not extend through valve 24, the blow-oil force could be opposed by a single hold-up motor arranged within distributing block and engaging valve 24 upon its vertical center line a short distance inward from the inner edge of the high pressure valve port but in that location it would occupy a part of the space required by shaft 2. Therefore, the blow-01f force is opposed by two spaced apart hold-up motors which are arranged in distributing block 25 and engage valve 24 at equal distances from the vertical center line. The two hold-up motors are the equivalent of and function in the same manner as a single hold-up motor arranged upon the vertical center line of the valve.
As shown in Figs. 3 and 4, two hold-up motors 40 and 4| are arranged in distributing block 25 above its horizontal center line and two hold-up motors 42 and 43 are arranged in distributing block 26 below its horizontal center line. All four hold-up motors are equidistant from the horizontal center line and are equidistant from the vertical center line. Also, auxiliary hold-up motors are ordinarily provided to compensate for variations in the blow-off area as explained in Patent No. 2,484,337 but such auxiliary motors have been omitted from the drawings to avoid complicating the views.
The four hold-up motors are identical and each has a hollow piston 44 fitted in a cylinder 45 which is formed in distributing block 25. Each piston 44 is urged by a spring 46 against an annular sealing member 41 which is urged by spring 46 against the outer end of valve 24, the contacting surfaces of member 41 and valve 24 being ground fiat and the contacting surfaces of piston 44 and member 41 being ground spherical to provide self-aligning liquid tight seals therebetween.
The openings through the pistons 44 and sealing members 41 of motors 40 and 4| communicate through passages 35 and chamber 33 with port 3 in valve 24 and the openings through the pistons 44 and sealing members 41 of motors 42 and 43 communicate through passages 36 and chamber 34 with port 32 in valve 24. The cylinders of motors 46 and 4| are connected by a passage 48 (Fig. 4) to each other and to a passage 49 which extends outward through distributing block 25 for connection to one side of an external circuit. The cylinders 45 of motors 42 and 43 are connected by a passage 50 to each other and to a passage 5| which extends outward through distributing block 25 for connection to the other side of an external circuit.
The force exerted upon pistons 44 by springs 46 is transmitted to valve 24 and any pressure prevailing in the hold-up motor cylinders acts upon the ends of pistons 44 and is transmitted therethrough to valve 24. Consequently, valve 24 is urged against its seat 26 by the constant force supnlied'by the four springs 44 and by a force which varies in accordance with variations in the pressure of the motive liquid.
Valve 24 is identical to valve 24 and distributing block 25'- is identical to distributing block 25. Consequently, they have not been fully illustrated and a description thereof is deemed unnecessary, like parts and passages as far as shown being indicated by like reference numerals with the exponent a added to the reference numerals applied to valve 24- and distributing block 25.
Passage 49 in block 25 and passage 49 in block 25 are connected to each other by a channel 52. Passage 5| in block 25 and passage 5| in block 25'- are connected to each other icy a channel 53.
Channels 52 and 53 have been shown as external channels and as being connected, respectively, by channels 54and 55 to opposite ends of a. hydraulic motor 56 but in practice they may be formed in the casing of the machine and connected to a different device.
Passages 8 and 8 are equally spaced in the cylinder barrel 4 and valves 24 and 24"- are symmetrical about their horizontal center lines so that, when cylinder barrel 4 is rotated, the mahin will fu ction as a pump and will deliver liquid in a direction and at a rate. dependent upon the direction and rate of rotation of cylinder barrel 4 and upon the direction and distance slide block I2 is ofiset from its neutral position, it being understood that, when slide block I2 is in its neutral position so that thrust member III is concentric with cylinder barrel 4, pistons I and 1' will not be reciprocated and no liquid will be delivered by the pump.
Assuming that cylinder barrel 4 is being rotated in a clockwise direction in respect to Fig. 1 and that slide block i2 is oiiset to the left of its neutral position in respect to that figure, the pistons in the lower half of cylinder barrel 4 will move progressively outward and the pistons in the upper half of cylinder barrel 4 will be forced progressively inward by thrust member ii. The cylinders of the outward moving pistons will be filled with liquid which flows thereto through the passages 8 and 8" connected thereto, the lower parts of valves 24 and 24 and the lower parts of distributing blocks 25 and 25" from channel 53, the liquid being supplied to channel 53 from the external circuit and/or from an auxiliary pump according to common practice. The inward moving pistons will eject liquid from their cylinders through passages 8 and 3* connected thereto, the upper parts of valves 24 and 24', the upper parts of distributing blocks 25 and 25', channel 52 and channel 54 to the external circuit and the resistance encountered by the liquid in the external circuit will cause pressure to rise and act upon the pistons 44 of motors 46, 4|, 4!! and 4 I and cause them to urge valves 24 and 24 inward with a force proportional to pump pressure, thereby firmly holding valves 24 and 24* against their seats 26 and 26'.
If cylinder barrel 4 is rotated in the opposite direction or if slide block [2 is shifted to the other side of its neutral position, the pump will deliver liquid into channel 53, ports 32 and 32 will then be the high pressure ports, ports 3i and 3| will then be the low pressure ports, and the pressure in ports 32 and 32 will cause the pistons 44 of motors 42, 43, 42 and 43* to firmly hold valves 24 and 24 against their seats 26 and 26'.
During rotation of cylinder barrel 4, inclined valve seats 26 and 26 cause valves 24 and 24 to wabble and continuously reciprocate pistons 44 which are thus enabled to dislodge particles of matter which tend to accumulate between the walls of cylinders and pistons, thereby reducing to a minimum all danger of the hold-up pistons sticking in their cylinders.
Each piston 44 alternately draws liquid into and ejects liquid from its cylinder as it reciprocates therein. That is, pistons 44 pump liquid so that limited volumes of liquid are alternately subtracted from and added to the liquid dise charged from pump cylinders 6 and 6 and also the liquid supplied to pump cylinders 6 and 6.
If valve seats 25 and 26 are inclined in the same direction as shown in Fig. 2, each piston 44 at one end of the pump will draw liquid into its cylinder 45 at the same time and at the same rate that the corresponding piston 44 at the other end of the pump ejects liquid from its cylinder 45. Consquently, there will be no flow from hold-up cylinders 45 to an external circuit so that, if the pump were connected as shown in Fig. 2, piston 51 of motor 56 would be moved at a uniform rate when the pump had a positive displacement and it would remain stationary when the pump was at zero displacement.
Figure 6 When a prior pump which is connected in circuit with a hydraulic motor is adjusted from zero displacement to a positive displacement, the pump will start to deliver liquid at a limited rate but the motor will not start until after the pump has discharged enough liquid to compress the liquid between it and the motor piston and thereby create suflficient pressure in the motor to start it. There is thus a time lag between the adjustment of the pump and the starting of the motor, particularly if the motor is to be operated at slow speed in which case the pump is adjusted to deliver liquid at such a low rate that an appreciable length of time is required for the Pump to deliver sufilcient liquid to compress the liquid between it and the motor piston to the pressure required to start the motor. When the motor is employed for certain purposes, it is important that the motor starts substantially at the instant that the pump is adjusted to a positive displacement.
Substantially instantaneous starting of the motor in response to adjustment of the pump to a positive displacement in either direction, or to reversal of pump discharge by moving the slide block across neutral position, may be effected by inclining the pump valve seats 26 and 26 in opposite directions as shown in Fig. 6. With the valve seats inclined in opposite directions, rotation of cylinder barrel 4 will cause corresponding pistons 44 at opposite ends of the pump to be moved alternately toward and from each other.
During one hall! of each revolution of cylinder barrel 4, the pistons 44 above the horizontal center line of the pump will move outward and eject liquid from their cylinders and the pistons 44 below the horizontal center line of the pump will move inward and draw liquid into their cylinders.
During the other half of each revolution of cylinder barrel 4, the pistons 44 below the horizontal center line of the pum will move outward and eject liquid from their cylinders and the pistons 44 above the horizontal center line of the pump will move inward and draw liquid into their cylinders. A limited volume of liquid is thus alternately supplied to and subtracted from each side of the circuit in which the pump is connected but, when the pump is adjusted to a positive displacement, the net volumetric delivery of the pump is unaffected by the pumping action of hold-up pistons 44.
When the pump is ajusted to zero displacement and cylinder barrel 4 is rotated, pistons I and 1 wil not be reciprocated and no liquid will be discharged thereby but hold-up pistons 44 will be reciprocated in their cylinders. The outward moving pistons 44 will expel liquid from their cylinders into one side of the hydraulic circuit and the cylinders containing the inward moving pistons will be filled with liquid from the other side of the circuit.
If the pump and the motor are connected into a closed circuit and the parts are so proportioned that the volume of liquid discharged by the outward moving istons 44 into one side of the circuit is great enough to compress the liquid in that side of the circuit to create pressure therein but is not great enough to eiIect operation of the motor, the previously compressed liquid in the other side of the circuit will expand and fill the cylinders containing the inward moving pistons 44, it being understood that means are provided to make up leakage losses such as by connecting each side of the circuit to a low pressure auxiliary pump through check valves according to common practice and as shown in.
Patent No. 2,406,138 and in PatentNo. 2,484,337. In this case, there will be no actual flow in the circuit.
If the pump is connected into a closed bydraulic circuit with a reciprocating hydraulic motor as shown in Fig. 6 and the parts are so proportioned that the volume of liquid discharged by the outward moving pistons 44 into one side of the circuit is sufficient to compress the liquid therein and to cause the piston 51 of the motor to move slightly, the cylinders containing the inward moving pistons 44 will be filled with liquid by the expansion of the liquid in the other side of the circuit and by the liquid expelled by piston 51 from the motor cylinder. In this case there will be a slig t flow of liquid in opposite directions alternately and piston 51 will be vibrated rapidly, making one complete reciprocation during each revolution of cylinder barel 4.
In either case, the pulsations of pressure will follow each other very rapidly for the reason that cylinder barrel 4 is ordinarily rotated at high speed. For example, if cylinder barrel 4 is rotated at 1200 R. P. M. which is an ordinary speed, pressure will be created in both sides of the circuit alternately every of a second.
If at the instant that the pump is adjusted to deliver liquid into one side of the circuit the outward moving pistons are creating presure in the same side of the circuit, the motor will start at the same instant but, if at that instant the outward moving pistons 44 are creating pressure in the opposite side of the circuit, the motor will start as soon as cylinder barrel 4 has made one-- half or less of a revolution which in the above example would be of a second or less and that arranged upon each of the two opposite ends thereof and inclined to the plane of rotation thereof and passages extending from some of said cylinders through one of said valve seats and other passages extending from the other of said cylinders through the other of said valve seats, two flat valves engaging said seats respectively to control the flow of liquid to and from said cylinders, each of said valves having inlet and outlet ports with which each of said passages registers alternately during rotation of said cylinder barrel, hold-up motors for urging said valves against said seats and each including a piston and a cylinder, means providing reactances for said hold-up motors, the inclined valve seats causing said valves during rotation of said cylinder barrel to wabble and effect relative reciprocation of said hold-up motor pistons and cylinders, means for connecting said inlet ports to each other and to an external circuit, and means for connecting said outlet ports to each other and to an external circuit.
4. In a hydrodynamic machine, the combination of a rotatable cylinder barrel having pistons and cylinders arranged therein, beveled wear plates fixed upon opposite ends thereof and providing valve seats which are inclined to the plane of rotation thereof and passages extending from some of said cylinders through one of amount of time probably would be required to adjust the pump from zero to a positive displacement so that in any event the motor would start substantaneously instantaneously in response to adjustment of the ump.
The hydrodynamic machine disclosed herein is susceptible of various modifications and adapttations without departing from the scope of the invention which is hereby claimed as follows:
1. In a hydrodynamic machine, the combination of a rotatable cylinder barrel having pistons and cylinders arranged therein, a valve seat arranged upon an end thereof and inclined to the plane of rotation thereof and passages extending from said cylinders through said valve seat, a flat valve engaging said seat to control the now of liquid to and from said cylinders, hold-up motors for urging said valve against said seat and each including a piston and a cylinder, and means providing a reactance for said hold-up motors the inclined valve seat causing said valve duringrotation of said cylinder barrel to wabble and effect relative reciprocation of said hold-up motor pistons and cylinders.
2. In a hydrodynamic machine, the combination of a rotatable cylinder barrel having pistons and cylinders arranged therein, a beveled wear plate fixed upon an end thereof and providing a valve seat which is inclined to the plane of rotation thereof and passages extending from said cylinders through said valve seat, a flat valve engaging said seat to control the flow of liquid to and from said cylinders, hold-up motors for urging said valve against said seat and each including a piston and a cylinder, and means providing a reactance for said hold-up motors, the inclined valve seat causing said valve during rotation of said cylinder barrel to wabble and effect relative reciprocation of said hold-up motor pistons and cylinders.
3. In a hydrodynamic machine, the combination of a rotatable cylinder barrel having pistons and cylinders arranged therein, a valve seat said valve seats and other passages extending from the other of said cylinders through the other of said valve seats, two flat valves engaging said seats respectively to control the flow of liquid to and from said cylinders, each of said valves having inlet and outlet ports with which each of said passages registers alternately during rotation of said cylinder barrel, hold-up motors for urging said valves against said seats and each including a piston and a cylinder, means providing reactances for said hold-up motors, the inclined valve seats causing said valves during rotation of said cylinder barrel to wabble and effect relative reciprocation of said hold-up motor pistons and cylinders, means for connecting said inlet ports to each other and to an external circuit, and means for connecting said outlet ports to each other and to an external circuit.
5. In a hydrodynamic machine, the combination of a rotatable cylinder barrel having pistons and cylinders arranged therein, a valve seat arranged upon an end thereof and inclined to the plane of rotation thereof and passages extending from said cylinders through said valve seat, a fiat valve engaging said seat to control the flow of liquid to and from said cylinders and provided with inlet and outlet ports in the inner face thereof and with passages extending through the outer face thereof into communication with said ports, a stationary distributing block spaced from the outer face of said valve, and hold-up motors arranged in said block in alignment with said passages, each hold-up motor, including a cylinder having a connection for the flow of liquid to and from an external circuit, a hollow piston fitted in said cylinder and a hollow sealing member arranged between said piston and the outer face of said valve so that liquid flows through said hold-up motors to and from said cylinder barrel and any pressure in said liquid causes said pistons to urge said valve against said valve seat, said inclined valve seat during rotation of said cylinder barrel causing said valve to wabble and reciprocate said hold-up pistons to prevent them from sticking in their cylinders.
6. In a hydrodynamic machine, the combination of a rotatable cylinder barrel having pistons and cylinders arranged therein, a beveled wear plate fixed upon an end thereof and providing a valve seat which is inclined to the plane of rotation thereof and passages extending from said cylinders through said seat, a flat valve engaging said seat to control the flow of liquid to and from said cylinders and provided with inlet and outlet ports in the inner face thereof and with passages extending through the outer face thereof into communication with said ports, a stationary distributing block spaced from the outer face of said valve, and hold-up motors arranged in said block in alignment with said passages, each hold-up motor including a cylinder having a connection for the fiow of liquid to and from an external circuit, a hollow piston fitted in said cylinder and a hollow sealing member arranged between said piston and the outer face of said valve so that liquid flows through said hold-up motors to and from said cylinder barrel and any pressure in said liquid causes said pistons to urge said valve against said valve seat, said inclined valve seat during rotation of said cylinder barrel causing said valve to wabble and reciprocate said hold-up pistons to prevent them from sticking in their cylinders.
7. In a hydrodynamic machine, the combination of a rotatable cylinder barrel having a plurality of pistons and cylinders arranged therein, a valve seat arranged upon each of the two ends thereof and inclined to the plane of rotation thereof, passages leading from a part of said cylinders through one of said valve seats and other passages leading from the other cylinders through the other of said valve seats, two flat valves arranged at opposite ends of said cylinder barrel and engaging said seats to control the flow of liquid to and from,said cylinders and provided with inlet and outlet ports in the inner faces thereof and with passages extending through the outer faces thereof into communication with said ports, a stationary distributing block spaced from the outer face of each valve, and hold-up motors arranged in said blocks in alignment with said valve passages, each holdup motor including a cylinder having a connection for the flow of liquid to and from an external circuit, a hollow piston fitted in said cylinder and a hollow sealing member arranged between said piston and the outer face of the adjacent valve so that liquid flows through said hold-up motors to and from said cylinder barrel and any pressure in said liquid causes said pistons to urge said valves against said valve seats and said inclined valve seats during rotation of said cylinder barrel causes said valves to wabble and reciprocate said hold-up pistons to prevent them from sticking in their cylinders.
8. In a hydrodynamic machine, the combination of a rotatable cylinder barrel having a plurality of pistons and cylinders arranged therein,
beveled wear plates fixed upon opposite ends thereof and providing valve seats which are inclined to the plane of rotation thereof, passages leading from a part of said cylinders through one of said seats and other passages leading from the other cylinders through the other of said seats, two flat valves arranged at opposite ends of said cylinder barrel and engaging said seats to control the flow of liquid to and from said cylinders and provided with inlet and outlet ports in the inner faces thereof and with passages extending through the outer faces thereof into communication with said ports, a stationary distributins block spaced from the outer face of each valve, and hold-up motors arranged in said blocks in alignment with said valve passages, each hold-up motor including a cylinder having a connection for the flow of liquid to and from an external circuit, a hollow piston fitted in said cylinder and a hollow sealing member arranged between said piston and the outer face of said valve so that liquid flows through said hold-up motors to and from said cylinder barrel and any pressure in said liquid causes said pistons to urge said valves against said valve seat and said inclined valve seats during rotation of said cylinder barrel causes said valves to wabble and reciprocate said hold-up pistons to prevent them from sticking in their cylinders.
9. In a hydraulic transmission comprising a motor, fluid channels, and a pump connected to said motor by said channels to form therewith a hydraulic circuit and including a rotatable cylinder barrel having a plurality of pistons and cylinders arranged therein, the combination of a valve seat arranged upon each end of said cylinder barrel and inclined to the plane of rotation thereof, said cylinder barrel having passages leading from some of said cylinders through one of said valve seats and other passages leading from the other of said cylinders through the other valve seat, two flat valves arranged at opposite ends of said cylinder barrel and engaging said seats to control the flow of liquid to and from said cylinders and provided withinlet and outlet ports in the inner faces thereof and with passages extending through the outer faces thereof into communication with said ports, a stationary distributing block spaced from the outer face of each valve, and hold-up motors arranged in said blocks in alinement with said valve passages, each hold-up motor including a cylinder having a connection for the flow of liquid to and from said circuit, a hollow piston fitted in said cylinder and an annular sealing member arranged between said piston and the outer face of the adjacent valve so that liquid flows through said hold-up motors to and from said cylinder barrel and any pressure in said liquid causes said pistons to urge said valves against said valve seats, said inclined valve seats during rotation of said cylinder barrel causing said valves to wabble and reciprocate said hold-up pistons to prevent them from sticking in their cylinders and to cause each hold-up piston during reciprocation thereof to function as a pump and alternately increase and decrease the flow of liquid therethrough by a limited amount, said valve seats being inclined in opposite directions so that corresponding hold-up pistons at opposite ends of said cylinder barrel pump in the same phase and thereby. effect a pulsating flow of liquid to said motor.
10. In a hydraulic transmission comprising a motor, fluid channels, and a pump connected to said motor by said channels to form therewith a hydraulic circuit and including a rotatable cylinder barrel having a plurality of pistons and cylinders arranged therein. the combination of a beveled wear plate fixed upon each end of said cylinder barrel and providing a valve seat which is inclined to the plane of rotation of said cylinder barrel, said cylinder barrel having passages leading from some of said cylinders through one of said valve seats and other passages leading from the other of said cylinders through the other valve seat, two flat valves arranged at opposite ends of said cylinder barrel and engaging said seats to control the flow of liquid to and from said cylinders and provided with inlet and outlet ports in the inner faces thereof and with passages extending through the outer faces thereof into communication with said ports, a stationary distributing block spaced from the outer face of each valve, and hold-up motors arranged in said blocks in alinement with said valve passages, each hold-up motor including a cylinder having aconnection for the flow of liquid to and from said circuit, a hollow piston fitted in said cylinder and an annular sealing member arranged between said piston and the outer face of the adjacent valve so that liquid flows through said hold-up motors to and from said cylinder barrel and any pressure in saidliquid causes said pistons to urge said valves against said valve seats, said inclined valve seats during rotation of said cylinder barrel causing said valves to wabble and reciprocate said hold-up pistons to prevent them from sticking in their cylinders and to cause each hold-up piston during reciprocation thereof to function as a pump and alternately increase and decrease the flow of liquid therethrough by a limited amount, and said valve seats being inclined in opposite directions so that corresponding h d-up pistons at opposite ends of said cylinder rrel pump in the same phase and thereby effect a pulsating flow of liquid to said motor.
11. In a hydraulic transmission comprising a motor, fluid channels, and a pump connected to said motor by said channels to form therewith a hydraulic circuit and including a rotatable cylinder barrel having a plurality of pistons and cylinders arranged therein, the combination of a valve seat arranged-upon each end of said cylinder barrel and inclined to the plane of rotation thereof, said cylinder barrel having passages leading from some of said cylinders through one of said valve seats and other passages leading from the other of said cylinders through the other valve seat, two fiat valves arranged at opposite ends of said cylinder barrel and engaging said seats to control the flow of liquid to and from said cylinders and provided with inlet and outlet ports in the inner faces thereof and with passages extending through the outer faces thereof into communication with said ports, a stationary distributing block spaced from the outer face of each valve. and hold-up motors arranged in said blocks in alinement with said passages, each hold-up motor including a cylinder having a connection for the flow of liquid to and from an external circuit, a hollow piston fitted in said cylinder and a hollow sealing member arranged between said piston and the outer face of the adjacent valve so that liquid flows through said hold-up motors to and from said cylinder barrel and any pressure in said liquid causes said pistons to urge said valves against said valve seats, said inclined valve seats during rotation of said cylinder barrel causing said valves to wabble and reciprocate said holdup pistons to prevent them from sticking in their cylinders and to cause each hold-up piston during reciprocation thereof to function as a pump and alternately increase and decrease the flow of liquid therethrough by a limited amount, and said valve seats being inclined in the same direction to cause corresponding hold-up pistons at opposite ends of said cylinder barrel to pump in opposite phase and thereby neutralize the pumping effects of each other so that the flow of liquid to said motor is unaffected by reciprocation of said hold-up pistons.
12. In a hydraulic transmission comprising a motor, fluid channels, and a pump connected to said motor by said channels to form therewith a hydraulic circuit and including a rotatable cylinder barrel having a plurality of pistons and cylinders arranged therein, the combination of a beveled wear plate fixed upon each end of said cylinder barrel and providing a valve seat which is inclined to the plane of rotation of said cylinder barrel, said cylinder barrel having passages leading from some of said cylinders through one of said valve seats and other passages leading from the other of said cylinders through the other valve seat, two flat valves arranged at opposite ends of said cylinder barrel and engaging said seats to control the flow of liquid to and from said cylinders and provided with inlet and outlet ports in the inner faces thereof and with passages extending through the outer faces thereof into communication with said ports, a stationary distributing block spaced from the outer faces of each valve, and hold-up motors arranged in said blocks in alinement with said valve passages, each hold-up motor including a cylinder having a connection for the flow of liquid to and from said circuit, a hollow piston fitted in said cylinder and an annular sealing member arranged between said piston and the outer face of the adjacent valve so that liquid flows through said hold-up motors to and from said cylinder barrel and any pressure in said liquid causes said pistons to urge said valves against said valve seats, said inclined valve seats during rotation of said cylinder barrel causing said valves to wabble and reciprocate said hold-up pistons to prevent them from sticking in their cylinders and to cause each hold-up piston during reciprocation thereof to function as a pump and alternately increase and decease the flow of liquid therethrough by a limited amount, and said valve seats being inclined in the same direction to cause corresponding hold-up pistons at opposite ends of said cylinder barrel to pump in opposite phase and thereby neutralize the pumping efiects of each other so that the flow of liquid to said motor is unaffected by reciprocation of said hold-up pistons.
WALTER. FERRIS.
REFERENCES CITED The following references are of record in the file of this patent:
UNITED STATES PATENTS Number Name Date 1,256,501 Conradson Feb. 12, 1918 1,817,080 Howard Aug. 4, 1931 2,337,821 Huber Dec. 28, 1943 2,381,741 Grosser Aug. 7, 1945 2, 97,314 Grosser Mar. 26, 1946 ,406,138 Ferris Aug. 20, 1946 FOREIGN PATENTS Number Country Date 27,721 Great Britain Dec. 9, 1911 2,784 Great Britain Feb. 3, 1913 208,591 Great Britain Dec. 19, 1923
US612252A 1945-08-23 1945-08-23 Hydrodynamic machine Expired - Lifetime US2501165A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
US612252A US2501165A (en) 1945-08-23 1945-08-23 Hydrodynamic machine

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US612252A US2501165A (en) 1945-08-23 1945-08-23 Hydrodynamic machine

Publications (1)

Publication Number Publication Date
US2501165A true US2501165A (en) 1950-03-21

Family

ID=24452380

Family Applications (1)

Application Number Title Priority Date Filing Date
US612252A Expired - Lifetime US2501165A (en) 1945-08-23 1945-08-23 Hydrodynamic machine

Country Status (1)

Country Link
US (1) US2501165A (en)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2728302A (en) * 1951-04-05 1955-12-27 Oilgear Co Reduction of shocks and noise in power pumps
DE939487C (en) * 1951-08-21 1956-02-23 Hans Dipl-Ing Gastrow Star piston pump for driving presses and injection molding machines
DE1015689B (en) * 1955-04-05 1957-09-12 Crown Engineering & Dev Co Radial piston machine
US3015212A (en) * 1957-06-26 1962-01-02 Thompson Grinder Co Pump control
US5249512A (en) * 1992-05-18 1993-10-05 Christenson Howard W hydrostatic pump and motor

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB191127721A (en) * 1911-12-09 1912-06-13 Camille Barbey Improvements relating to Liquid Transmission Apparatus.
GB191302784A (en) * 1913-02-03 1913-05-29 Camille Barbey Improvements in Liquid Transmission Apparatus.
US1256501A (en) * 1914-02-03 1918-02-12 Conrad M Conradson Hydraulic variable-speed transmission.
GB208591A (en) * 1922-09-19 1923-12-19 Maurice Kerr Ingoldby Improvements in or relating to variable speed hydraulic transmission apparatus
US1817080A (en) * 1929-04-10 1931-08-04 George E Howard Transmission mechanism
US2337821A (en) * 1942-12-02 1943-12-28 Hydraulic Controls Inc Pump
US2381741A (en) * 1942-10-22 1945-08-07 Standard Machinery Company Pump or motor unit
US2397314A (en) * 1943-08-26 1946-03-26 Standard Machinery Company Pump or motor unit
US2406138A (en) * 1942-01-14 1946-08-20 Oilgear Co Hydrodynamic machine

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB191127721A (en) * 1911-12-09 1912-06-13 Camille Barbey Improvements relating to Liquid Transmission Apparatus.
GB191302784A (en) * 1913-02-03 1913-05-29 Camille Barbey Improvements in Liquid Transmission Apparatus.
US1256501A (en) * 1914-02-03 1918-02-12 Conrad M Conradson Hydraulic variable-speed transmission.
GB208591A (en) * 1922-09-19 1923-12-19 Maurice Kerr Ingoldby Improvements in or relating to variable speed hydraulic transmission apparatus
US1817080A (en) * 1929-04-10 1931-08-04 George E Howard Transmission mechanism
US2406138A (en) * 1942-01-14 1946-08-20 Oilgear Co Hydrodynamic machine
US2381741A (en) * 1942-10-22 1945-08-07 Standard Machinery Company Pump or motor unit
US2337821A (en) * 1942-12-02 1943-12-28 Hydraulic Controls Inc Pump
US2397314A (en) * 1943-08-26 1946-03-26 Standard Machinery Company Pump or motor unit

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2728302A (en) * 1951-04-05 1955-12-27 Oilgear Co Reduction of shocks and noise in power pumps
DE939487C (en) * 1951-08-21 1956-02-23 Hans Dipl-Ing Gastrow Star piston pump for driving presses and injection molding machines
DE1015689B (en) * 1955-04-05 1957-09-12 Crown Engineering & Dev Co Radial piston machine
US3015212A (en) * 1957-06-26 1962-01-02 Thompson Grinder Co Pump control
US5249512A (en) * 1992-05-18 1993-10-05 Christenson Howard W hydrostatic pump and motor

Similar Documents

Publication Publication Date Title
US2608933A (en) Hydrodynamic machine
US3174436A (en) Radial pump
US3654761A (en) Fluid handling device with radially variable working chambers
US2680412A (en) Variable volume variable pressure pump
US2484337A (en) Hydrodynamic machine
US2827859A (en) Hydraulic pump
US2661701A (en) Axial type hydrodynamic machine
US3173376A (en) Hydraulic pump or motor
US2501165A (en) Hydrodynamic machine
US2820417A (en) Fluid pressure energy translating device
GB1224265A (en) Improvements in and relating to a rotary, positive-displacement pump
US2757612A (en) Axial piston pump
US3626810A (en) Variable reversible piston pump
US3457873A (en) Pumping chamber decompression
US2765749A (en) Fluid pump or motor
US3626981A (en) Rotary slide valve
US1749058A (en) Rotary pump
US3163121A (en) Piston pumps
US2466623A (en) Hydraulic axial vane pump or motor
US3036558A (en) Wobble plate fluid motor and single valve means
US3433124A (en) Hydraulic motor
US2006880A (en) High pressure radial piston hydraulic pump or motor
US3435775A (en) Hydraulic pump or motor
US3070030A (en) Pump
US3253410A (en) Fluid pressure power transmission system