US3374712A - Hydraulic radial piston machines - Google Patents

Hydraulic radial piston machines Download PDF

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Publication number
US3374712A
US3374712A US545155A US54515566A US3374712A US 3374712 A US3374712 A US 3374712A US 545155 A US545155 A US 545155A US 54515566 A US54515566 A US 54515566A US 3374712 A US3374712 A US 3374712A
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US
United States
Prior art keywords
pintle
pistons
pressure
rotor
piston
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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
US545155A
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English (en)
Inventor
Bjorklund Gustaf Erik
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.)
REDERI SOYA AB
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REDERI SOYA AB
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Publication date
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • 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
    • F01B1/0696—Controlling by changing the phase relationship between the actuating or actuated cam and the distributing means
    • 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
    • F01B13/062—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 cylinder block and actuating or actuated cam both rotating

Definitions

  • a hydraulic radial piston machine comprises a central pintle serving as a valve for the working medium, a rotor mounted on the pintle, and pistons radially movable in cylinder spaces in the rotor. These spaces communicate with the pintle through ports, the rotor defining with the pintle an intake passage and a discharge passage, the cylinder spaces communicating with those passages through the ports.
  • a track ring is mounted eccentrically of the pintle and rotor and surrounds the rotor and bears against the pistons to cause the pistons to reciprocate in the rotor upon rotation of the rotor.
  • the pintle is provided with a holder mounted for movement in a direction to vary the eccentricity of the machine and for movement substantially at right angles to that direction.
  • pistons are provided which are slidable in the holder, one of the pistons being urged away from the holder by the pressure of the high-pressure passage and the other of the pistons being urged away from the holder by the pressure of the low-pressure passage.
  • differences in pressure in the intake and discharge passages are utilized to move the ring and the pintle relative to each other in an amount and in a direction such that the angle between the diametrical plane in which the ports begin to open into the intake and discharge passages and the diametrical plane in which the pistons reverse increases with increasing pressure difference.
  • Hydraulic radial piston machines of the type under consideration comprise a central pintle serving as a valve for the working medium, a rotor mounted on the pintle and having pistons radially movable in cylinder spaces each of which has a port which cooperates with the pintle and during rotation of the rotor on the pintle successively opens into and is shut off from an intake passage and a discharge passage in the pintle, and a track ring mounted in the casing of the machine eccentrically with respect to the pintle and surrounding the rotor.
  • the ring bears against the pistons such that the pistons during rotation of the rotor reciprocate in the cylinders between outer and inner dead centers.
  • Variation of the stroke volume in such a radial piston machine is usually effected by translational displacement of the rotor and the pintle with respect to the ring or in other words by variation of the eccentricity of the ring.
  • the port of any cylinder will be closed on two occasions during each revolution, namely, when the port passes a cylindrical portion of the pintle between the inlet side and the outlet side thereof and also when the port passes another cylindrical portion on the opposite side of the pintle at the transition from the outlet side to the inlet side of the pintle.
  • the cylindrical portions of the pintle which cooperate with the port of the working cylinder are circumferentially wider than the peripheral width of the port.
  • the invention is characterized in that the pintle together with the rotor in addition to the conventional possibility of displacement with respect to the ring for varying the eccentricity of the ring and consequently the stroke volume of the machine is further adjustable with respect to the ring in response to the difference between the pressures of the working medium in the intake passage and discharge passage such that the angle between the diametrical plane in which the ports begin to open into the intake and discharge of the pintle and the diametrical plane in which the pistons reverse increases with decreasing eccentricity and vice versa.
  • FIGS. 1, 2, 3 and 4 are diagrammatic cross-sectional views of essential parts of a radial piston machine and explain the basic principle of the invention.
  • FIGS. 5, 6 and 7 illustrate a constructional embodiment, FIG. 6 being a central longitudinal section, FIG. 5 across-section along the line 5-5 in FIG. 6, and- FIG. 7 a cross-section along the line 77 in FIG. 6.
  • numeral 10 denotes the pintle of a radial piston pump having a rotor 12 and two diametrically opposite cylinders 14, 16 with pistons 18, 20 which are reciprocable in the cylinders by means of a surrounding track ring indicated by a circle 22.
  • the common axis of the rotor and the pintle is indicated at 24 and the axis of the track ring is indi cated at 26.
  • the pintle 10 has diametrically opposite recesses 28, 30, the recess 28 being in communication with the intake or low pressure side of the pump Whereas the recess 30 is in communication with the discharge or high pressure side of the pump.
  • the chain-dotted line AA denotes the diametrical plane in which the pistons reverse and which hereinbelow is referred to as the eccentricity plane.
  • the liquid in the cylinders and the material of the surrounding parts of the machine were entirely rigid it would be suitable if the inner ends or ports of the cylinders would pass from the suction side to the pressure side or vice versa exactly in the eccentricity plane where the pistons have their dead centers. In practical constructions it is not possible, however, to obtain other than more or less elastic systems.
  • the machine itself is slightly elastic, but above all the liquid has a certain compressibility. At an increase of pressure of about 2000 p.s.i. a hydraulic oil is compressed by approximately 1%. When the piston is in its outer dead center the oil has not yet been compressed in the cylinder. If the cylinder at that moment would be put into communictaion with the high pressure side where the pressure is f.i. 2000 p.s.i. oil
  • the compression and expansion under consideration can be obtained if the pe- 'ripheral surface 32 of the pintle which is passed by the than the port and if the pintle is turned through a certain angle a in the direction of rotation, as is shown in pressed in the cylinder 14 and expanded in the cylinder 16 to such a degree that the pressure in the cylinders at the high pressure passage and low pressure passage of the pintle, then no pressure shocks will arise. If the eccentricity of the track ring is changed from the greater value E shown in FIG. 1 to the smaller value E shown in FIG. 2 a greater angular deflection m of the pintle is required to obtain a certain piston movement at the desired compression.
  • AS is equal for two opposite pistons only if the working volumes inwardly of the pistons are equal, i.e.,"if the eccentricity E is zero. In all other positions the compression AS and the expansion AS do not correspond to each other. However, if AS is chosen such as to be the'right one on the compression side for maximum eccentricity the expansion after a revolution of 180 will 7 port 34 of the cylinder is of greater peripheral extension 7 7 the opening moment is equal to the respective pressure in I be driven so far that a small void will be formed below 7 the piston, but this involves practically no loss.
  • a maximum negative pressure of 14 p.s.i. during a piston movement of some tenths of a millimeter implies a very small loss of energy, but a noise occurs when the communication is opened and the void is filled. However, the volumes of the voids and the noises are very small.
  • FIG. 3 is a sectional view of the pintle 10 having recesses 28 and 30 on the low pressure side and high pressure side, respectively, and also shows part of the rotor 12.having two diametrically opposite inlet ports 34 to a pair of cylinders. The direction of rotation of the rotor is indicated at 36. With increasing pressure on the pressure side the pintle 10 should be turned in the direction of rotation.
  • FIG. 4 shows three' different positions B, B and B of said common axis.
  • FIGS. 5 to 7 illustrates a practical application of the principles indicated above.
  • a holder 42 for the pintle 10 is displaceable for varying the strokes of the pistons 18, 20 disposed in a rotor 12 of a radial piston machinein which the track ring 22 is secured to a shaft 44 mounted in the casing 40.
  • Displacement of the holder 42 is effected by 7 means of a lever 46 which is mounted on a pivot 48 in the casing of the machine and connected with the holder by an articulated rod 50.
  • the pump has an intake passage 28 and a discharge passage 30.
  • a radial cylinder .52 Provided on the high pressure side of the holder 42 is a radial cylinder .52
  • the piston On its outer. side the piston has a.
  • the magnitude of the force by which the working pistons 84, 86 on the high pressure side of the machine act upon the pintle in the direction a indicated in FIG. 7 depends upon the pressure of the working medium, the diameters of the working pistons and the number of the pistons.
  • the pintle 10 is moved slightly in a direction counter to the direction a, i.e., in the direction b in FIG. 7.
  • the force exerted by the adjusting piston 66 must be greater than the opposite resultant of the forces exerted by the working pistons on the pintle.
  • the magnitude of the adjusting displacements will be understood from the fact that in a machine having a piston stroke of 16 mm. the displacement is approximately 1 mm. at a pressure of about 2800 p.s.i. gauge.
  • the spring washers 56, 68 can be precompressed so that the washers on both sides are compressed in the whole pressure range.
  • the desired adjustment of the angle a is obtained at any position of the holder 42 of the pintle, i.e., at any adjusted piston stroke, due to the fact that with a'certain lateral displacement of the pintle by means of the adjusting pistons 54, 66 the angle on automatically will be increased with decreasing eccentricity and vice versa.
  • a hydraulic radial piston machine comprising a central pintle serving as a valve for the working medium, a rotor mounted on the pintle, pistons radially movable in cylinder spaces in the rotor, said spaces communicating with the pintle through ports, the rotor defining with the pintle an intake passage and a discharge passage, the cylinder spaces communicating with said passages through said ports, a track ring mounted eccentrically of the pintle and rotor and surrounding the rotor and bearing against the pistons to cause the pistons to reciprocate in the rotor upon rotation of the rotor; the improvement comprising a holder for the pintle, means mounting the holder for movement in a direction to vary the eccentricity of the machine, and means mounting the holder for movement substantially at right angles to said direction, said right-angle movement means comprising pistons slidable in the holder, one of the pistons being urged away from the holder by the pressure of the high-pressure passage and the other of the pistons being urged away from the
  • a machine as claimed in claim 3 the machine having a stationary casing, and means acting between the casing and the pistons to precompress the spring means.
  • a machine as claimed in claim 1 the machine having a stationary casing, and thrust members disposed between the pistons and the casing.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Hydraulic Motors (AREA)
  • Reciprocating Pumps (AREA)
US545155A 1965-05-05 1966-04-25 Hydraulic radial piston machines Expired - Lifetime US3374712A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
SE588665 1965-05-05

Publications (1)

Publication Number Publication Date
US3374712A true US3374712A (en) 1968-03-26

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Family Applications (1)

Application Number Title Priority Date Filing Date
US545155A Expired - Lifetime US3374712A (en) 1965-05-05 1966-04-25 Hydraulic radial piston machines

Country Status (3)

Country Link
US (1) US3374712A (tr)
GB (1) GB1104604A (tr)
NL (1) NL6606037A (tr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4927338A (en) * 1987-03-02 1990-05-22 Nippondenso Co., Ltd. Radial piston pump

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1398788A (en) * 1919-11-12 1921-11-29 Taylorwharton Iron And Steel C Rotary pump or motor
US1518851A (en) * 1922-05-25 1924-12-09 Hutchison George Herbert Hydraulic pump and motor
US2179071A (en) * 1938-04-09 1939-11-07 Oilgear Co Control for hydrodynamic machines
US3051092A (en) * 1959-01-06 1962-08-28 United Aircraft Corp Pump torque limiting means
US3188918A (en) * 1962-04-04 1965-06-15 Soya Rederi Ab Rotary machine having a fluidworking medium

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1398788A (en) * 1919-11-12 1921-11-29 Taylorwharton Iron And Steel C Rotary pump or motor
US1518851A (en) * 1922-05-25 1924-12-09 Hutchison George Herbert Hydraulic pump and motor
US2179071A (en) * 1938-04-09 1939-11-07 Oilgear Co Control for hydrodynamic machines
US3051092A (en) * 1959-01-06 1962-08-28 United Aircraft Corp Pump torque limiting means
US3188918A (en) * 1962-04-04 1965-06-15 Soya Rederi Ab Rotary machine having a fluidworking medium

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4927338A (en) * 1987-03-02 1990-05-22 Nippondenso Co., Ltd. Radial piston pump

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Publication number Publication date
GB1104604A (en) 1968-02-28
NL6606037A (tr) 1966-11-07

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