EP0234134A1 - Dispositif rotatif de commutation de fluide - Google Patents

Dispositif rotatif de commutation de fluide Download PDF

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Publication number
EP0234134A1
EP0234134A1 EP86400387A EP86400387A EP0234134A1 EP 0234134 A1 EP0234134 A1 EP 0234134A1 EP 86400387 A EP86400387 A EP 86400387A EP 86400387 A EP86400387 A EP 86400387A EP 0234134 A1 EP0234134 A1 EP 0234134A1
Authority
EP
European Patent Office
Prior art keywords
notches
fluid
switching device
openings
rotary fluid
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.)
Withdrawn
Application number
EP86400387A
Other languages
German (de)
English (en)
Inventor
Yasuo Kita
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.)
Shimadzu Corp
Original Assignee
Shimadzu Corp
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 Shimadzu Corp filed Critical Shimadzu Corp
Priority to EP86400387A priority Critical patent/EP0234134A1/fr
Publication of EP0234134A1 publication Critical patent/EP0234134A1/fr
Withdrawn legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/20—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
    • F04B1/2014—Details or component parts
    • F04B1/2042—Valves
    • F04B1/205—Cylindrical
    • 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
    • F03C1/06—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinder axes generally coaxial with, or parallel or inclined to, main shaft axis
    • F03C1/0636—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinder axes generally coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
    • 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
    • F03C1/06—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinder axes generally coaxial with, or parallel or inclined to, main shaft axis
    • F03C1/0636—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinder axes generally coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
    • F03C1/0644—Component parts
    • F03C1/0655—Valve means
    • F03C1/0657—Cylindrical valve means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/20—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block

Definitions

  • the present invention relates to a rotary fluid switching device adapted for use, for example, in a fluid passage in a rotary fluid energy converter, such as a hydraulic pump or motor.
  • Rotary fluid switching devices has been mounted in fluid passages in hydraulic pumps or motors of the radial piston type, bent axis type, or swash plate type to cause a working fluid to be continuously distributed to, and discharged from, cylinders.
  • a rotary fluid switching device of this kind is shown in Fig. 5 and presents a block d with its valve surface a provided with a port b for high pressure and a port c for low pressure, for supplying and discharging fluid.
  • the switching device further presents a cylinder block g provided with ports f circumferentially spaced apart from each other in its valve surface e that comes into sliding contact with the port block d.
  • the ports f periodically establish and interrupt communication with the ports b and c.
  • Devices of this type often have notches h and i (see also Fig. 6) extending away from ends of the ports b and c in order to reduce the shock occurring when the system is switched from high pressure to low pressure or vice versa, and to cut down on noise and vibration.
  • the notches h and i are located on the median circle line k of the ports b and c, which means that the center j of each port f travels over the notches h and i. This tends to reduce the volumetric efficiency for the following reason.
  • the formation of the notches h and i generally tends to produce erosion at those locations on the valve surface e of the cylinder block g over which travel the notches h and i. Therefore, the erosion progressively extends along the line k connecting each center j of the ports f on the valve surface e of the cylinder block g.
  • the line k connecting each center j of the ports f provides the shortest distance between any two circumferentially adjacent ports f. Accordingly, such an extension of the erosion results in that the adjacent ports f rapidly establish communication with each other via the eroded portion, frequently leading to a decrease in the volumetric efficiency. For this reason, one is dissuaded to arrange the ports f in close adjacent position.
  • a rotary fluid switching device having a first valve surface provided with fluid supply and discharge openings and a second valve surface being in sliding contact with said first valve surface and provided with circular or elliptic cylinder ports that are spaced from one another in the direction of rotation, said two valve surfaces being rotated relative to each other so that the cylinder ports alternately establish and interrupt communication with the openings, characterized in that at least one notch extends at least one end of said openings, said notch being located off the line along which each center of the cylinder ports travels.
  • a pair of notches extend each end of said openings, both notches being located off the line along which each center of the cylinder ports travels.
  • the two notches of each said pair are different in length, so that the fluid communication simultaneously occurs and interrupts for both notches and the width in cross section of each notch gradually decreases away from its corresponding opening end.
  • the erosion develops along locations lying off the median line connecting each center of the cylinder ports. Since said median line provides the shortest distance between adjacent cylinder ports, the risk of fluid leaking from one cylinder port to the adjacent one is thus effectively prevented. Hence, the volumetric efficiency does not deteriorate.
  • a rotary fluid energy converter incorporating a rotary fluid switching device according to the invention as described later.
  • This energy converter comprises a torque ring 2 that is rotatably and closely held against the inner surface of a housing 1 via first static pressure bearings 3.
  • the housing 1 is shaped as a cone with a bottom portion, and is provided at one end with an opening 1a.
  • a tapering surface 4 that tapers off toward the opening 1a is formed in the portion of the inner surface of the housing 1 supporting the ring 2.
  • the ring 2 is shaped like a cup, and has an outer peripheral wall 2a presenting the same apical angle as the tapering surface 4.
  • a rotating shaft 6 protrudes away from one end of the axially central portion of the ring 2. The front end of the shaft 6 extends outwardly from the housing 1 through the opening 1a.
  • Flat surfaces 2c are formed on the portions of the inner surface of the ring 2 which are opposite to the first surface pressure bearings 3.
  • the first static pressure bearings 3 have shoes 5 rigidly secured to the outer periphery of the ring 2 at required positions.
  • the shoes 5 are attached to the tapering surface 4 of the housing 1.
  • Each shoe 5 is provided with pressure pockets 7 into which fluid pressure is introduced.
  • An odd number of pressure bearings 3 are circumferentially regularly spaced from one another.
  • Pistons 8 are disposed at locations corresponding to the flat surfaces 2c of the inner surface of the ring 2.
  • the front ends 8a of the pistons 8 are connected to their respective inner surfaces 2c via second static pressure bearings 9 whose active surfaces are made flat so that the front ends 8a of the pistons 8 are in intimate contact with the inner surfaces 2c.
  • Pressure pockets 11 are formed in the front ends 8a, and fed with pressure fluid.
  • a pintle 14 and an annular cylinder barrel 15 rotatably fitted over the outer periphery of the pintle 14 are mounted inside the torque ring 2.
  • the axis n of the pintle 14 is parallel to the axis m of the housing 1.
  • the pintle 14 has a sliding portion 14a guided by the housing 1.
  • the barrel 15 is equipped with cylinders 16 which are circumferentially regularly spaced from one another.
  • the axes of the cylinders 16 are substantially perpendicular to the outer periphery of the pintle 14.
  • the pistons 8 are fitted in the respective cylinders 16 so as to be slidable.
  • the bottom end surfaces 8b of the pistons 8 cooperate with the inner surfaces of the cylinders 16 to delimit chambers 13 for introduction and discharge of fluid.
  • the cylinder barrel 15 is connected to the torque ring 2 by means of an Oldham coupling 20 or similar means, and rotates at the same angular velocity as the ring 2.
  • the contour of the pintle 14 takes the form of a truncated cone presenting substantially the same apical angle as the peripheral wall 2a of the ring 2.
  • the pistons 8 are held in such a way that they can move back and forth perpendicularly to said peripheral wall 2a of the ring 2.
  • the sliding portion 14a of the pintle 14 is shaped into a vertically elongated block of trapezoidal cross section.
  • the housing 1 is formed with a trapezoidal groove 19 in which the sliding portion 14a is fitted so as to be slidable. In other words, the pintle 14 is so held as to be slidable in a direction perpendicular to the axis m of the housing 1. This makes it possible to adjust the distance D between the axis n of the pintle 14 and the axis m of the housing 1 to any desired value, including zero.
  • the inside of the housing 1 is divided into a first region A and a second region B by an imaginary line P drawn in the direction in which the pintle 14 slides.
  • Any chamber 13 moving across the first region A communicates with a first fluid communication passage 21.
  • Any chamber 13 passing across the second region B communicates with a second communication passage 22.
  • the first fluid communication passage 21 comprises cylinder ports 23, a port 24 extending through the pintle 14, and a fluid inlet/outlet port 25 formed in the housing 1.
  • the ports 23 permit the chambers 13 to communicate with the inner surface 15v, or valve surface, of the cylinder barrel 15.
  • One end of the port 24 extends to the outer periphery 14v, or valve surface, of the pintle 14 in the first region A, while the other end extends to an inclined surface 14b of the sliding portion 14a of the pintle 14 in the second region B.
  • the port 25 extends to the other end of the port 24.
  • Formed at said one end of port 24 is a pressure pocket 27 for supply and discharge of fluid.
  • This pocket 27 is used to form a third static pressure bearing 26 between the outer periphery (valve surface) 14v of the pintle 14 and the inner surface (valve surface) 15v of the cylinder barrel 15.
  • a pressure pocket 29 Formed at the other end of the port 24 is a pressure pocket 29 forming a fourth static pressure bearing 28 between the inclined surface 14b of the pintle 14 and the inner surface of the housing 1.
  • the pocket 27 is elongated circumferentially, and acts to place all the chambers 13 present in the first region A in communication with the port 24 extending through the pintle.
  • the pocket 29 is elongated in the direction in which the pintle 14 slides, and serves to prevent the inlet/outlet port 25 from being disconnected from the port 24 when the pintle 14 is sliding.
  • the second fluid communication passage 22 comprises the aforementioned cylinder ports 23, a port 34 extending through the pintle 14, and a fluid inlet/outlet port 35 formed in the housing 1.
  • One end of the port 34 extends to the outer periphery (valve surface) 14v of the pintle 14 in the second region B, while the other end extends to an inclined surface 14c of the sliding portion 14a of the pintle in the first region A.
  • the inlet/outlet port 35 corresponds in position to the other end of the port 34.
  • a pressure pocket 37 for supply and discharge of fluid is formed at one end of the port 34. This pocket 37 is also used to form a third static pressure bearing 36 between the pintle 14 and the cylinder barrel 15.
  • a pressure pocket 39 Formed at the other end of the port 34 is a pressure pocket 39 that is employed to form a fourth static prssure bearing 38 between the inclined surface 14c of the pintle 14 and the inner surface of the housing 1.
  • These pressure pockets 37 and 39 are similar in structure to the pressure pockets 27 and 29.
  • the fluid pressure within the chambers 13 corresponding to the pistons 8 is guided into the pressure pockets 11 of the corresponding second static pressure bearing 9 via a pressure inlet passage 41 formed along the axis of each piston 8. Then, the fluid pressure inside the pockets 11 is directed to the pressure pockets 7 of the corresponding first static pressure bearing 3 via a fluid passage 42 formed in the torque ring 2.
  • the directions and areas of the bearings 3 and 9 are so set that the force acting on the ring 2 due to the static pressure of the fluid introduced into the first bearings 3 is equal in magnitude but opposite in direction to the force acting on the ring 2 due to the static pressure of the fluid introduced into the second bearings 9.
  • the area of the second bearings 9 is set to such a value that the force acting on the pistons 8 due to the static pressure of the fluid introduced into the second bearings 9 is cancelled by the force acting on the pistons 8 due to the static pressure of the fluid inside the chambers 13.
  • the area of the third static pressure bearings 26 and 36 is set to such a value that the force acting on the cylinder barrel 15 due to the static pressure introduced into the bearings 26 and 36 is cancelled by the force acting on the barrel 15 due to the static pressure of the fluid within the chambers 13 extending in the repective regions A and B.
  • the angle at which the surfaces 14b and 14c having the fourth bearings 28 and 38 are inclined is set to such a value that the force acting on the pintle 14 due to the static pressure of the fluid introduced into the fourth bearings 28 and 38 is cancelled by the force acting on the static pressure of the fluid introduced into the third bearings 26 and 36 existing in the respective regions A and B corresponding to the inclined surfaces 14b and 14c.
  • the sliding portion 14a of the pintle 14 is biased in one direction by a spring 45, and can be moved in the opposite direction against the action of the spring 45 by a hydraulic actuator 46.
  • a pressure-­compensation valve 47 is switched to its other state whereby to supply working high-pressure fluid to the actuator 46.
  • the fundamental operation of the fluid energy converter is described in Japanese laid-open patent specification n o 77179/1983. Specifically, when a high-pressure fluid is supplied into the chambers 13 existing in the first region A via the first fluid communication passage 21, a couple is produced which induces rotation of the torque ring 2 in the direction indicated by the arrow S. Thus, the converter acts as a motor. When the ring 2 is rotated by an external force in the direction indicated by the arrow R, the high-­pressure fluid is discharged from the first passage 21. Accordingly, the converter acts as a pump. When the eccentricity of the axis n of the pintle 14 from the axis m of the housing 1 is changed by moving the pintle 14 back and forth along the trapezoidal groove 19, the displacement is varied.
  • a rotary fluid switching converter 51 embodying the concept of the invention is mounted between the pintle 14 and the cylinder barrel 15.
  • the converter 51 comprises the valve surface 14v of the pintle 14 and the valve surface 15v of the cylinder barrel 15, and these surfaces 14v and 15v are in sliding contact with each other.
  • the openings 27 and 37 for supply and discharge of fluid extend up to the valve surface 14v.
  • the circular cylinder ports 23 are circumferentially spaced from one another on the valve surface 15v. As the valve surfaces 14v and 15v are rotated relative to each other, the cylinder ports 23 periodically establish and interrupt communication with the openings 27 and 37.
  • a pair of small notches 52 and 53, is formed at ends of the openings 27 and 37.
  • the fluid switching device 51 is constructed as described hereabove, even if an erosion occurs on the valve surface 15v of the barrel 15 because of the presence of the notches 52 and 53, the erosion will develop off the line 54 connecting each center of the cylinder ports 23, being noted that the line 54 provides the shortest distance between adjacent ports 23. Therefore, it is unlikely that fluid leaks from one port 23 to an adjacent one 23, so that the volumetric efficiency is also unlikely to be reduced. Hence, it is possible to arrange the ports 23 closer to each other than in conventional devices.
  • two notches are formed at each end of the openings for supply and discharge of fluid.
  • the invention is not limited to this arrangement.
  • only one notch may be formed off the center line 54 of the cylinder ports for each end.
  • formation of a pair of notches at each end of the openings as in the illustrated embodiment reduces still more effectively occurrence of erosion. Whether an erosion occurs easily or not depends on the fluid velocity, or the kinetic energy of the fluid.
  • the fluid velocity obtained when two notches are formed at each end as in the illustrated embodiment is half of the fluid velocity obtained when only one notch is formed at each end. For this reason, with the former arrangement, erosion is less likely to occur. Obviously, it is not necessary that all the ends of openings for supply and discharge of fluid have notches.
  • the fluid switching device is mounted between the pintle and the cylinder barrel fitted over the pintle.
  • the present invention is not necessarily limited to such an arrangement.
  • it can be similarly applied to an arrangement where the fluid switching device is mounted between a port block or plate having a flat valve surface and a cylinder block as shown in Fig. 5.
  • the invention is applicable to fluid switching sections in pumps and motors of the ordinary radial piston type, bent axis type, or swash plate type.
  • the shape of the notches is not limited to the shape used in the illustrated embodiment. Various changes and modifications may be made thereto without departing from the scope of the invention.
  • openings for supply and discharge of fluid also serve as pressure pockets for balancing the static pressure, but the invention is not limited to such a scheme.
  • the novel rotary fluid switching device is constructed as described hereabove, the simple structure effectively prevents deterioration in the volumetric efficiency, in spite of the existence of notches.
  • the intended performance can be maintained over a long working life.
  • it allows cylinder ports to be arranged closely without secondary drawback.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Reciprocating Pumps (AREA)
  • Hydraulic Motors (AREA)
EP86400387A 1986-02-24 1986-02-24 Dispositif rotatif de commutation de fluide Withdrawn EP0234134A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP86400387A EP0234134A1 (fr) 1986-02-24 1986-02-24 Dispositif rotatif de commutation de fluide

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP86400387A EP0234134A1 (fr) 1986-02-24 1986-02-24 Dispositif rotatif de commutation de fluide

Publications (1)

Publication Number Publication Date
EP0234134A1 true EP0234134A1 (fr) 1987-09-02

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP86400387A Withdrawn EP0234134A1 (fr) 1986-02-24 1986-02-24 Dispositif rotatif de commutation de fluide

Country Status (1)

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EP (1) EP0234134A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103591017A (zh) * 2013-11-11 2014-02-19 南昌尊荣泵业有限公司 一种中高压径向球头柱塞泵

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2047557A1 (de) * 1969-10-06 1971-04-22 VEB Kombinat Orsta Hydraulik Be trieb Industnewerke Karl Marx Stadt, χ 9030 Karl Marx Stadt Hydrostatische Kolbenmaschine

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2047557A1 (de) * 1969-10-06 1971-04-22 VEB Kombinat Orsta Hydraulik Be trieb Industnewerke Karl Marx Stadt, χ 9030 Karl Marx Stadt Hydrostatische Kolbenmaschine

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103591017A (zh) * 2013-11-11 2014-02-19 南昌尊荣泵业有限公司 一种中高压径向球头柱塞泵

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Inventor name: KITA, YASUO