US3874271A - Radial piston machine - Google Patents

Radial piston machine Download PDF

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Publication number
US3874271A
US3874271A US322086A US32208673A US3874271A US 3874271 A US3874271 A US 3874271A US 322086 A US322086 A US 322086A US 32208673 A US32208673 A US 32208673A US 3874271 A US3874271 A US 3874271A
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United States
Prior art keywords
piston
shoes
pistons
recesses
combination
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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
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US322086A
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English (en)
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Karl Eickmann
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    • 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
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/10—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement the cylinders being movable, e.g. rotary
    • 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
    • F01B1/0641—Details, component parts specially adapted for such machines
    • F01B1/0644—Pistons

Definitions

  • the invention relates to P -1 Piston Shoes and 9589- [58] Field of Search 91/491-498, ciated safety means in fluid handling devices including 91 4 43 439; 417 273 hydraulic or pneumatic pumps, motors and transmissions, wherein recesses for the reception of portions of [56] R fere Ci d the piston shoes are provided in a fluid handling body UNITED STATES PATENTS and the walls which are adjacent to the recesses serve I to prevent the escape of piston shoes from the recesses, wherein convex and concave semispherical en- 8/194; Glasner gagement surfaces are provided on the pistons and pis- 511991460 8/1965 Bush ct 111.21: I: 11:: 91/494 Shoes and wherein Piston Stroke enlargement 3,223,046 12/1965 Eickmann 1 91/488 means and friction Preventing means y be associ- 3.274.946 9/1966 Simmons 91/486 at with h piston shoes
  • the guides for the piston shoes create a certain amount of friction between the neighboring faces which reduces the efficiency of the device.
  • the machining of the piston-piston shoe connection is complex and expensive and, most of all, the piston-piston shoe connection takes up space either on the piston or on the piston shoe, for an engagement means which holds the pivotable piston and piston shoe together. Therefore, only a portion of the crosssectional area of the piston can be utilized for transmitting force from the piston to the piston shoe or from the piston shoe to the piston during the high pressure stroke of the device.
  • the other portion of the cross-sectional area of the piston is needed for the retaining means or the retaining member, which partially embraces either the piston shoe or the piston for keeping them together.
  • a piston shoe or the like has a cross-sectional area greater than that of the piston, its radial length must be increased which in turn reduces the stroke and thereby the power of the device having a fluid handling body ofa given diameter.
  • the limited portion of the cross-sectional area ofthe piston can presently be used for the transmission of power from the shoe to the piston or from the piston to the shoe during a high pressure stroke reduces the maximum power transfer at the same ratio as the ratio of the cross-sectional area utilized for the power transfer to the cross-sectional area of the piston. Consequently the pressure which could be generated in the known devices is limited by the utilized cross-sectional area and therefore, the pressure and power output of conventional devices are limited.
  • each piston shoe which may include a hollow cone for the reception of the respective piston
  • FIG. 1 is an axial sectional view of a fluid handling device which embodies one form of the invention
  • FIG. 2 is a cross-sectional view of the structure shown in FIG. 1;
  • FIG. 3 is an axial sectional view of a fluid handling device which embodies another form of the invention.
  • FIG. 4 is a cross sectional sectional view of the structure shown in FIG. 3;
  • FIG. is a sectional view of portions of a modified piston and piston shoe.
  • FIG. 6 is a fragmentary axial sectional view of a further embodiment of the fluid handling body.
  • the fluid handling body 9 has cylinders 47 wherein the pistons 2 reciprocate during operation of the device.
  • the pistons are associated to piston shoes 1 which engage the piston heads during the pressure strokes of the respective pistons.
  • Each piston head is formed as a half ball or as a half mound bar with an axis normal to the axis of the piston.
  • the piston head face has a constant radius, about the same as the associated piston shoe seat of the piston shoe 1. Consequently the piston shoe has a seat face which conforms to the piston head at least during the high pressure stroke of the piston.
  • the piston shoes seat face has therefore also a constant radius and thereby either the form of about a half hollow ball or of a half hollow cylinder.
  • the seats of each piston head and of the associated piston shoe are complementary to each other.
  • the piston shoe seat 44 may extend into a tapered, conical, or inclined face or faces serving the purpose of centering the piston shoe on the respective piston head, if-the piston and piston shoe are forced toward each other.
  • the fluid handling body 9 has recesses 4 for the reception of portions of or entire piston shoes. Securing walls 3 flank the recesses to prevent escape of the piston shoes.
  • the piston shoes 1 have enlarged extensions 45 with walls 5 which would touch the walls 3 of the recesses 4 if the piston shoes would become separated from the respective pistons during rest or during a low pressure operation of the device.
  • the walls 3, 5 prevent escape of piston shoes from the respective recesses 4.
  • the piston shoes are secured in axial direction against escape from the recesses 4 by confining walls 29 and 31 of the housing.
  • a space 46 is provided between the walls 5 of the elargements 45 and the walls 3 of the recess 4 as well as between the axial ends of the piston shoes 1 and the walls 29 and 31.
  • the piston shoes 1 have pressure balancing recesses 7 which receive fluid through passages 8 and prevent the generation of high friction between the inner faces of the piston shoes 1 and the outer face or guide face 6 of the actuator means 11.
  • the actuator means 11 effects the high pressure strokes of the pistons 2 and piston shoes 1 when the actuator means 11 is actuated by the drive means 12 and key means 13.
  • the pistons 2 perform intake strokes under the action of fluid supplied by supercharger pump means 17.
  • inlet valve 14 and an exit valve 15 is associated with each cylinder 47 of the fluid handling device.
  • inlet valve 14 and an exit valve 15 for each recess 4 of the fluid handling device.
  • the body of the fluid handling drive is a stator
  • the body of the fluid handling device of FIGS. 3 and 4 is a rotor
  • the fluid handling rotor 40 is rotatable on the shaft 13 and is received in a housing 28 having end walls 29 and 32. Cylinders 26 are provided in the rotor 40 for the reception of portions of the pistons 2 Fluid is passed through the end wall 32 via ports 33 and 34. One of the ports 33, 34 is the inlet port and the other the outlet port. The fluid flows through passages 38 and 39 of a control body 36-37 into and out of the cylinders 26.
  • the rotor 40 has recesses 23 for piston shoes 1.
  • the piston shoes have outer faces 21 which slide along the inner face 22 of an actuator means 28 which compels successive pistons and shoes to perform inward strokes.
  • the piston shoes perform outward strokes either by centrifugal force during rotation of the rotor 40 or by compressed fluid entering the cylinders 26 and 47.
  • Walls 46 bounding the recesses 23 prevent the escape of piston shoes tangentially of the recesses because the piston shoe extensions 45 are so long that they cannot move over the walls 46 of the recesses 23.
  • the escape of the piston shoes 1 axially and out of recesses 23 is prevented by the securing wall means 29 and 31 disposed at the axial ends ofthe recesses 23.
  • the wall means 29 may have a thrust bearing 30 for the rotor 40 and the wall means 29 and 31 may have radial bearings for the shaft 13 and rotor 40.
  • the piston shoes have outer recesses 41 for admission of fluid from the cylinders 26 through passages 8 of pistons 2.
  • the cylinders 26 have walls 25 which extend to their outer ends for guiding and sealing the pistons 2.
  • FIGS. 3 and 4 An important feature of the device of FIGS. 3 and 4 is that a large piston stroke and thereby a high rate of fluid flow and big power is assured. This is assured by the extensions 24 which form part of the recesses 23 and extend radially inwardly into the rotor 40 beyond the outer ends 25 of the cylinders 26 for the reception of the inward extensions 92 of the piston shoes 1 so that the extensions 92 of the piston shoes can enter the rotor 40 beyond the outer ends of the cylinders 26. In order to demonstrate the difference between the provision and the absence of the extensions 24, the upper recess 23 in FIG. 4 is shown without such inwardly extending extension.
  • the semispherical piston head 49 is complementary to the hollow semispherical piston shoe seat 48 and abuts thereagainst so that the force can be transmitted from the piston to the piston shoe or from the piston shoe to the piston, while at the same time the piston shoe 1 can pivot upon the piston head relative to the respective piston 2 during operation of the device while the outer face of the shoe 1 and its balancing recess 41 slide along the inner actuator face of the stationary or rotary actuator means (ring or housing) 28.
  • the recess 41 is provided in the piston head to eliminate or reduce friction between the piston shoe and the housing.
  • the piston shoe portion above the piston head is kept as short as possible in order to provide a long piston stroke and thereby a high rate of fluid flow.
  • the cross sections through the recesses 4, 23 and through the piston shoes 1 normal to the axes of the pistons 2 may be of cylindrical or rectangular configuration. Consequently the recesses 4 or 23 are either cylinders or cubes. In FIGS. 1 to 4 the recesses 4 and 23 are shown in the form of cubes, meaning axially extending rectangular recesses through the fluid handling 9 or rotor 40.
  • This configuration is prefered, because it is less expensive in production than a cylindrical configuration.
  • a cylindrical configuration requires individual production of each recess 4 or 23 while a rectangular recess 4 or 23 can be pressed or cut at the same time through a number of axially aligned and stacked fluid handling bodies 9 or 40.
  • the outer configurations of a large number of piston shoes complementary to such rectangular recesses can be produced at the same time by pressing, material extrusion or drawing. These configurations make therefor the piston shoes especially inexpensive.
  • FIG. 5 shows that the fluid receiving and fluid containing pressure balancing recess 148 in the head of the piston 2 may have a cross-sectional area almost the size of the cross-sectional area of the piston 2. ln praxis the area of the recess 148 is about 60 to 90 percent of that of the piston 2. Thereby the friction between the piston 2 and the piston shoe 1 is very substantially reduced. Such large sizes of balancing recesses 148 of 90 percent of the cross-sectional area of the piston 2 can be achieved only by the novel forms of the piston 2 and piston shoe 1.
  • FIG. 6 shows that the fluid handling body 91 may be a rotor surrounded by a rotary actuator ring 28 however, the body 91 and ring 28 could also be stationary if so desired.
  • the FIG. 6 further shows that the fluid handling body 91 may be a double or multi-cylinder group device for one or more flows of fluid through its cylinder groups 147 and 247.
  • the recesses 23 for the reception of piston shoes 1 are then flanked by walls 83 and 84 secured to the fluid handling body 91 and/or by a wall or walls 82 integral with the fluid handling body 91.
  • the actuator ring 28 may be provided with an annular groove 81 for re ception of a portion of the wall 82 and the walls 83 and 84 may extend radially outwardly partially beyond the inner face of the actuator ring 28.
  • Recesses or extensions can be provided radially on the fluid handling body 9, 40 or 91 or on the actuator means 11, 28 peripherally of the piston shoes 1 for preventing their escape out of the recesses 4 or 23 in response to very long piston strokes. The said extensions may then temporarily extend into said recesses. The latter are not shown in the figures because they may be provided in any suitable portion of the means whereon they are provided.
  • the fluid handling device of the invention produces a high pressure, insures long piston strokes, high rate of flow of fluid, good efficiency and great power and is easy to build, inexpensive in production and very reliable in operation for long periods of time because friction is eliminated or reduced to a considerable extent.
  • a combination comprising a housing; a fluid handling body member provided in said housing and having substantially radially extending cylinders; an actuator member provided in said housing and having an endless guide surface, one of said members surrounding the other of said members; pistons reciprocably mounted in said cylinders and defining with said body member variable-volume working chambers remote from said guide surface, said chambers forming part of the respective cylinders and having inlets for admission and outlets for evacuation of a fluid medium; piston shoes associated with said pistons and slidable along said guide surface in response to rotation of one of said members relative to the other of said members to thereby reciprocate said pistons in the respective cylinders, at least a portion of each of said shoes having a polygonal cross sectional outline and said body member having polygonal recesses receiving said portions of said shoes with sufficient clearance to at least temporarily afford to said portions of said shoes the freedom of limited tilting movement in at least two different directions so as to enable said shoes to follow said endless guide surface of said actuator member while the machine is in
  • said curved surfaces are substantially hemispherical surfaces, one thereof being convex and the other thereof being concave and said concave surfaces having conical extensions.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
US322086A 1972-01-07 1973-01-08 Radial piston machine Expired - Lifetime US3874271A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
AT13772A AT337004B (de) 1972-01-07 1972-01-07 Radialkolben-maschine - pumpe oder motor - mit stationarem oder mit rotierendem zylinderblock

Publications (1)

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US3874271A true US3874271A (en) 1975-04-01

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US322086A Expired - Lifetime US3874271A (en) 1972-01-07 1973-01-08 Radial piston machine

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US (1) US3874271A (de)
JP (1) JPS597033B2 (de)
AT (1) AT337004B (de)
DE (1) DE2300569C2 (de)

Cited By (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4475870A (en) * 1980-08-19 1984-10-09 Karl Eickmann Hydraulic arrangement
US4557347A (en) * 1981-07-14 1985-12-10 Karl Eickmann Fluid pumps, fluid motors and devices, wherein they are applied
US4626177A (en) * 1980-08-19 1986-12-02 Karl Eickmann Hydraulic arrangement
US4690623A (en) * 1978-05-31 1987-09-01 Karl Eickmann Fluid pumps, fluid motors and devices, which include a coned ring
US4690620A (en) * 1980-08-19 1987-09-01 Karl Eickmann Variable radial piston pump
US4776768A (en) * 1986-08-09 1988-10-11 Nippondenso Co., Ltd. Radial plunger pump driven by a motor having seal members for protecting the motor from exposure to working fluid
US4776258A (en) * 1974-11-29 1988-10-11 Karl Eickmann Radial piston machine with pistons and piston shoes between faces
US4927338A (en) * 1987-03-02 1990-05-22 Nippondenso Co., Ltd. Radial piston pump
US5004406A (en) * 1988-03-23 1991-04-02 Nippondenso Co., Ltd. Radial piston pump
US5364234A (en) * 1992-05-20 1994-11-15 Karl Eickmann High pressure devices
US6347574B1 (en) * 1998-01-23 2002-02-19 Robert Bosch, Gmbh Radial piston pump for producing high pressure fuel
US20080031744A1 (en) * 2004-05-13 2008-02-07 Peter Boehland High-Pressure Pump for a Fuel Injection System of an Internal Combustion Engine
US20080066614A1 (en) * 2006-09-15 2008-03-20 Chia-Peng Lo Pneumatic rotary motor without connecting rods
US20080213114A1 (en) * 2005-04-22 2008-09-04 George Miller Pump

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4037523A (en) * 1974-11-29 1977-07-26 Karl Eickmann Application of an entering or deep-diving piston shoe with a central radial support member and means for securing the same in fluid handling radial piston devices
DE3419741A1 (de) * 1984-05-26 1985-11-28 Otto 8399 Ruhstorf Wimmer Hochdruck-kolbenpumpe
DE102024203484A1 (de) * 2024-04-15 2025-10-16 Hawe Hydraulik Se Radialkolbenpumpe

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2236666A (en) * 1936-02-26 1941-04-01 Elek K Benedek Fluid pressure power pump or motor
US2276368A (en) * 1940-10-17 1942-03-17 Midland Machine Corp Lubrication of radial pumps or motors
US2356993A (en) * 1943-02-04 1944-08-29 Midwest Hydraulics Inc Radial pump
US3199460A (en) * 1962-01-11 1965-08-10 Stewart Warner Corp Hydraulic pump or motor
US3223046A (en) * 1961-10-13 1965-12-14 Eickmann Karl Rotary radial piston machines
US3274946A (en) * 1964-04-13 1966-09-27 Edward E Simmons Pump
US3628425A (en) * 1968-12-13 1971-12-21 Messrs Mitsubishi Jukogyo Kk Fluid motor-pump construction
US3650180A (en) * 1969-09-30 1972-03-21 Arinc Res Corp Compound hydrostatic bearing for rotary radial piston hydraulic machines
US3663125A (en) * 1970-11-23 1972-05-16 Lucas Industries Ltd Hydraulic pump

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB574991A (en) * 1944-02-15 1946-01-29 Precision Developments Co Ltd Improvements in radial pumps
DE837206C (de) * 1947-09-18 1952-04-21 Schweizerische Lokomotiv Kolben fuer mit Fluessigkeit betriebene Kolbenmaschinen
GB1211637A (en) * 1968-05-10 1970-11-11 Stella Metal Filters Ltd Drainage element for filtering device

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2236666A (en) * 1936-02-26 1941-04-01 Elek K Benedek Fluid pressure power pump or motor
US2276368A (en) * 1940-10-17 1942-03-17 Midland Machine Corp Lubrication of radial pumps or motors
US2356993A (en) * 1943-02-04 1944-08-29 Midwest Hydraulics Inc Radial pump
US3223046A (en) * 1961-10-13 1965-12-14 Eickmann Karl Rotary radial piston machines
US3199460A (en) * 1962-01-11 1965-08-10 Stewart Warner Corp Hydraulic pump or motor
US3274946A (en) * 1964-04-13 1966-09-27 Edward E Simmons Pump
US3628425A (en) * 1968-12-13 1971-12-21 Messrs Mitsubishi Jukogyo Kk Fluid motor-pump construction
US3650180A (en) * 1969-09-30 1972-03-21 Arinc Res Corp Compound hydrostatic bearing for rotary radial piston hydraulic machines
US3663125A (en) * 1970-11-23 1972-05-16 Lucas Industries Ltd Hydraulic pump

Cited By (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4776258A (en) * 1974-11-29 1988-10-11 Karl Eickmann Radial piston machine with pistons and piston shoes between faces
US4690623A (en) * 1978-05-31 1987-09-01 Karl Eickmann Fluid pumps, fluid motors and devices, which include a coned ring
US4626177A (en) * 1980-08-19 1986-12-02 Karl Eickmann Hydraulic arrangement
US4475870A (en) * 1980-08-19 1984-10-09 Karl Eickmann Hydraulic arrangement
US4690620A (en) * 1980-08-19 1987-09-01 Karl Eickmann Variable radial piston pump
US4557347A (en) * 1981-07-14 1985-12-10 Karl Eickmann Fluid pumps, fluid motors and devices, wherein they are applied
US4776768A (en) * 1986-08-09 1988-10-11 Nippondenso Co., Ltd. Radial plunger pump driven by a motor having seal members for protecting the motor from exposure to working fluid
US4927338A (en) * 1987-03-02 1990-05-22 Nippondenso Co., Ltd. Radial piston pump
US5004406A (en) * 1988-03-23 1991-04-02 Nippondenso Co., Ltd. Radial piston pump
US5364234A (en) * 1992-05-20 1994-11-15 Karl Eickmann High pressure devices
US6347574B1 (en) * 1998-01-23 2002-02-19 Robert Bosch, Gmbh Radial piston pump for producing high pressure fuel
US20080031744A1 (en) * 2004-05-13 2008-02-07 Peter Boehland High-Pressure Pump for a Fuel Injection System of an Internal Combustion Engine
US7513190B2 (en) * 2004-05-13 2009-04-07 Robert Bosch Gmbh High-pressure pump for a fuel injection system of an internal combustion engine
US20080213114A1 (en) * 2005-04-22 2008-09-04 George Miller Pump
US20080066614A1 (en) * 2006-09-15 2008-03-20 Chia-Peng Lo Pneumatic rotary motor without connecting rods

Also Published As

Publication number Publication date
JPS597033B2 (ja) 1984-02-16
DE2300569A1 (de) 1973-08-30
DE2300569C2 (de) 1986-06-12
ATA13772A (de) 1976-09-15
AT337004B (de) 1977-06-10
JPS4874601A (de) 1973-10-08

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