US3876343A - Rotary piston machine for liquids - Google Patents

Rotary piston machine for liquids Download PDF

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Publication number
US3876343A
US3876343A US383891A US38389173A US3876343A US 3876343 A US3876343 A US 3876343A US 383891 A US383891 A US 383891A US 38389173 A US38389173 A US 38389173A US 3876343 A US3876343 A US 3876343A
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United States
Prior art keywords
ports
ring
chambers
centrally located
valve part
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
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US383891A
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English (en)
Inventor
Svend Giversen
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Danfoss AS
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Danfoss AS
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
    • F04C2/103—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member one member having simultaneously a rotational movement about its own axis and an orbital movement
    • F04C2/104—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member one member having simultaneously a rotational movement about its own axis and an orbital movement having an articulated driving shaft
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
    • F04C2/103—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member one member having simultaneously a rotational movement about its own axis and an orbital movement
    • F04C2/105—Details concerning timing or distribution valves

Definitions

  • ABSTRACT The invention relates to a fluid pressure operated motor or pump of the type having a gerotor displacement mechanism. Such devices normally have a separate valve member for directing pressurized fluid from the casing inlet to the expanding chambers of the gerotor and exhaust fluid from collapsing chambers to the casing outlet.
  • valve member there is no separate valve member and a unique valve passage ar rangcment is provided in a stationary casing port wherein a centrally located port is surrounded by a ring of ports.
  • the centrally located port may be the inlet or outlet port and the ring of ports is the opposite thereof.
  • the invention relates to a rotary piston machine for liquids having a toothed wheel and a toothed ring which surrounds the toothed wheel.
  • Said toothed ring having one more tooth than the wheel and forming displacement chambers with the wheel, a distributor valve comprising two parts one of which is coupled to one of the toothed elements and has first control openings which overlap second control openings in the other valve part and connecting ducts which lead from the second control openings to the displacement chambers.
  • the object of the present invention is to provide a rotary piston machine, the distributor valve of which is of very simple, space saving construction and is particularly suitable for small machines.
  • this object is achieved by a rotary piston machine having two sets of control openings. One of said sets is connected to the supply line and the other to the discharge line. The difference in the positioning of the two sets relative to the eccentricity of the movement of one of the toothed elements provides a commutator type fluid feeding and exhausting arrangement.
  • the advantage of a machine of this kind resides in the fact that the two parts of the distributor valve are firmly connected to the toothed wheel and to the toothed ring or can even be formed directly on one of these toothed elements.
  • a disadvantage is that the distributor valve gives a poorer control performance than distributor valves having two parts arranged concentrically with each other. In particular, during transition from one set of the first control openings to the other, the second control openings are completely covered over a greater angle of rotation of the associated toothed element.
  • this distributor valve When, however, this distributor valve is used as a primary distributor valve in conjunction with a secondary distributor valve, 21 machine of simple construction and having an accurate control function is obtained.
  • one set is formed by a central bore and the other set is in surrounding relation thereto.
  • the toothed wheel prefferably has a central cavity in which is fitted an insert incorporating the second control openings.
  • the portions of the connecting duct formed in the insert and in the toothed wheel being at an angle to each other. This results in the control opening being connected to a displacement chamber offset through 90; the connecting duct however does not interfere with the adjacent control opening.
  • the insert consists of two parts, one of which incorporates the portions of the connecting duct, and the other the second control openings.
  • FIG. 1 is a longitudinal section through a motor in accordance with the invention
  • FIG. 2 is a side view, on a greater scale, of the toothed elements and the control openings, one displacement chamber being seen at its maximum size, and
  • FIG. 3 is an illustration similar to that of FIG. 2 showing one displacement chamber at its minimum size.
  • the rotary piston machine has a casing l to one end face of which a cover plate 3 is secured by means of screw bolts 2, while at its other end face an intermediate plate S, a toothed ring 6, an intermediate plate 7 and a connection plate 8 are secured by means ofscrew bolts 4.
  • a main shaft 9 is mounted in the casing 1. This shaft is connected to a toothed wheel 11 through a universal joint shaft 10.
  • the toothed wheel 11 has four teeth 12, and the toothed ring 6 has five teeth I3 in the form of cylindrical rollers.
  • Displacement chambers 14 are formed between these teeth and the intermediate plates 5 and 7.
  • the displacement chambers 14 are connected through a valving arrangement in the correct working manner to two ports 15 and 16 in the plate 8 associated with the supply and discharge lines.
  • This valving arrangement is represented by a distributor valve 17 in which a first stationary port is the plate 7, and a second movable port is the wheel 11 and inserts 27 and 28 fastened thereto so as to be integral therewith.
  • Plate 7 constitutes a valve plate with a central bore I8 which is directly connected to the port 15, and five openings 19 along a circle concentric with port I5 which openings 19 are connected to the port 16 by way of an annular channel 20 in the connection plate 8.
  • the bore 18 and the circle of control openings I9 are disposed concentrically with the central axis of the toothed ring 6.
  • Four openings 21 are provided in inserts of the toothed wheel, and these openings are disposed along a circle around the central axis of the toothed wheel 11.
  • the control openings I9 extend in the peripheral direction. Their inwardly directed limiting edge 22 runs tangentially to a circle concentric with the bore 18.
  • the lines 23, 24, 25 and 26 defining the control openings 21 are so selected that, in the position illustrated in FIG. 2 in which one displacement chamber 14 is at its maximum volume, said lines extend parallel to the limiting line 22 of the control openings 19 and thus lie between the bore 18 and these control openings 19.
  • the second control openings 21 are provided in a first insert part 27, which part, together with a second insert part 28, is accommodated in a cavity 29 in the toothed wheel 11.
  • first connecting duct portions 30 which take the form of channels and are covered by the first insert part 27.
  • second connecting duct portions 31 Provided in the toothed wheel 11 are second connecting duct portions 31 and these extend from the periphery of the cavity 29 to the base of the gap between two consecutive teeth.
  • the two connecting duct portions 30 and 31 are at an angle to each other.
  • Auxiliary ducts 32 are also provided on the toothed wheel 11. They take the form of channels at the two end faces of the toothed wheel and are disposed on the flanks of each tooth. They extend over a distance such that they each enable a connection between adjacent displacement chambers 14 to be established, this connection however being interrupted by the remaining tooth configuration bearing on the tooth of the toothed ring 6 in the zone of the line of symmetry S.
  • the chambers b and c are under return pressure
  • the toothed wheel 11 and consequently the main shaft 9 are therefore turned in the clockwise direction.
  • the toothed wheel occupies the position shown in FIG. 3 in which the chamber a is at its minimum size.
  • the auxiliary ducts 32 each connect adjacent chambers b and c, and d and 0, but this connection is cut off in the zone of the line S of symmetry of the toothed ring.
  • the return pressure should be communicated to the chamber a as rapidly as possible. This is achieved by connecting the chamber a to the chamber b through an auxiliary duct 32. No importance therefore attaches to the size of the angle through which the toothed wheel must turn before the right hand control opening 21 associated with the chamber a at this moment moves into contact with the control opening 19.
  • auxiliary ducts 32 in the flanks of the teeth of the toothed wheel, there are other types of auxiliary ducts which may be utilized.
  • a fluid pressure motor comprising an internally toothed ring gear having an axis, a cooperating externally toothed star gear having fewer teeth than said ring gear disposed eccentrically relative to said ring gear axis, said star gear having rotational movement about its own axis and orbital movement about the axis of said ring gear with the teeth of said gears intermeshing in sealing engagement to form expanding chambers on one side of a rotating line of symmetry and contracting chambers on the other side of said line during relative movement between said gears, an end wall fixedly attached to said ring gear and forming fixed wall means for said chambers, valve means comprising a first valve part formed by said end wall and a second movable valve part integral with said star gear, a first set of inlet and outlet fluid ports in said first valve part comprising a centrally located port surrounded by a ring of ports, said centrally located port being one of said ports and said ring of ports being the remaining ones of said ports, said second valve part having a single set of ports arranged in

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Hydraulic Motors (AREA)
  • Rotary Pumps (AREA)
US383891A 1972-08-18 1973-07-30 Rotary piston machine for liquids Expired - Lifetime US3876343A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE2240632A DE2240632C2 (de) 1972-08-18 1972-08-18 Rotationskolbenmaschine für Flüssigkeiten

Publications (1)

Publication Number Publication Date
US3876343A true US3876343A (en) 1975-04-08

Family

ID=5853901

Family Applications (1)

Application Number Title Priority Date Filing Date
US383891A Expired - Lifetime US3876343A (en) 1972-08-18 1973-07-30 Rotary piston machine for liquids

Country Status (10)

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US (1) US3876343A (enrdf_load_stackoverflow)
JP (1) JPS5332525B2 (enrdf_load_stackoverflow)
BE (1) BE802032R (enrdf_load_stackoverflow)
CH (1) CH582833A5 (enrdf_load_stackoverflow)
DD (1) DD106440A6 (enrdf_load_stackoverflow)
DE (1) DE2240632C2 (enrdf_load_stackoverflow)
FR (1) FR2196678A6 (enrdf_load_stackoverflow)
GB (1) GB1408806A (enrdf_load_stackoverflow)
IT (1) IT1059810B (enrdf_load_stackoverflow)
SE (1) SE391007B (enrdf_load_stackoverflow)

Cited By (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4145167A (en) * 1976-02-17 1979-03-20 Danfoss A/S Gerotor machine with pressure balancing recesses in inner gear
US4219313A (en) * 1978-07-28 1980-08-26 Trw Inc. Commutator valve construction
US4357133A (en) * 1978-05-26 1982-11-02 White Hollis Newcomb Jun Rotary gerotor hydraulic device with fluid control passageways through the rotor
US4474544A (en) * 1980-01-18 1984-10-02 White Hollis Newcomb Jun Rotary gerotor hydraulic device with fluid control passageways through the rotor
US4502855A (en) * 1982-11-24 1985-03-05 Danfoss A/S Rotary piston machine with parallel internal axes
US4597725A (en) * 1982-11-24 1986-07-01 Danfoss A/S Rotary piston machine with parallel internal axes
US4859160A (en) * 1987-09-18 1989-08-22 White Hollis Newcomb Jun Cutaway rotor gerotor device
US4872819A (en) * 1978-05-26 1989-10-10 White Hollis Newcomb Jun Rotary gerotor hydraulic device with fluid control passageways through the rotor
US4877383A (en) * 1987-08-03 1989-10-31 White Hollis Newcomb Jun Device having a sealed control opening and an orbiting valve
US4981422A (en) * 1987-07-27 1991-01-01 White Hydraulics, Inc. Gerotor device having a valve opening diameter smaller than the drive connection diameter
US5215453A (en) * 1991-04-15 1993-06-01 Danfoss A/S Gear wheel assembly for hydraulic purposes, and method assembling the same
US5516268A (en) * 1995-07-25 1996-05-14 Eaton Corporation Valve-in-star motor balancing
WO2003074874A1 (en) * 2002-03-05 2003-09-12 Sauer-Danfoss Aps Hydraulic machine
US20060067849A1 (en) * 2004-09-28 2006-03-30 Aisin Seiki Kabushiki Kaisha Rotor structure of inscribed gear pump
US20070092392A1 (en) * 2005-10-20 2007-04-26 Aisin Seiki Kabushiki Kaisha Internal gear pump
US20070292295A1 (en) * 2006-06-15 2007-12-20 White Drive Products, Inc. Rotor with cut-outs
US20150050176A1 (en) * 2011-11-24 2015-02-19 Zhengjiang Dali Hydraulic Motor Co., Ltd. Cycloidal Pinwheel Pair with Uniform Contact and One-tooth Difference

Families Citing this family (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2606172C2 (de) * 1976-02-17 1983-12-22 Danfoss A/S, 6430 Nordborg Rotationskolbenmaschine für Flüssigkeiten
DE2714114A1 (de) * 1977-03-30 1978-10-12 Rexroth Gmbh G L Drehkolbenmaschine
DE2829417C3 (de) * 1978-07-05 1984-07-12 Mannesmann Rexroth GmbH, 8770 Lohr Arbeitsmittelsteuerung für eine parallel- und innenachsige Rotationskolbenmaschine
DE2915361C2 (de) * 1979-04-14 1982-03-11 Maschinenfabrik Wagner GmbH & Co KG, 5203 Much Hydraulischer Kraftschrauber
CA1217089A (en) * 1982-03-23 1987-01-27 Hollis N. White, Jr. Rotary gerotor hydraulic device with fluid control passageways through the rotor
DE3249829C2 (en) * 1982-11-24 1990-01-18 Danfoss A/S, Nordborg, Dk Parallel and internal axis rotary piston engine
DE3248638C2 (de) * 1982-12-30 1985-01-03 Danfoss A/S, Nordborg Hydraulische Steuervorrichtung für einen Servomotor, insbesondere für Fahrzeuglenkungen
US4741681A (en) * 1986-05-01 1988-05-03 Bernstrom Marvin L Gerotor motor with valving in gerotor star
DE3861468D1 (de) * 1987-01-28 1991-02-14 Eaton Corp Ventil fuer sternmotor mit zwei geschwindigkeiten.
DE3869737D1 (de) * 1987-11-07 1992-05-07 Barmag Barmer Maschf Innenzahnradpumpe.
US6126424A (en) * 1998-05-19 2000-10-03 Eaton Corporation Transistion valving for gerotor motors
DE10056976C2 (de) * 2000-11-17 2002-12-05 Sauer Danfoss Holding As Nordb Hydraulische Maschine, insbesondere Motor
DE10056975C2 (de) * 2000-11-17 2002-12-05 Sauer Danfoss Holding As Nordb Hydraulische Maschine, insbesondere Pumpe

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2985110A (en) * 1956-11-19 1961-05-23 Bendix Corp Pump construction
US2989951A (en) * 1959-04-29 1961-06-27 Germane Corp Rotary fluid pressure device
US3233524A (en) * 1962-09-05 1966-02-08 Germane Corp Fluid operated motor
US3698841A (en) * 1970-12-21 1972-10-17 Webster Electric Co Inc Hydraulic motor

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH109955A (de) * 1924-02-22 1925-05-01 Hill Compressor & Pump Co Inc Zahnräder-Rotationsmaschine.
US3106163A (en) * 1960-04-04 1963-10-08 Roper Hydraulics Inc Pumps, motors and like devices
US3627454A (en) * 1969-07-14 1971-12-14 Trw Inc Hydraulic device
DE2124006C3 (de) * 1971-05-14 1979-03-01 Danfoss A/S, Nordborg (Daenemark) Rotationskolbenmaschine für Flüssigkeiten mit einem außenverzahnten und einem innenverzahnten Zahnrad

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2985110A (en) * 1956-11-19 1961-05-23 Bendix Corp Pump construction
US2989951A (en) * 1959-04-29 1961-06-27 Germane Corp Rotary fluid pressure device
US3233524A (en) * 1962-09-05 1966-02-08 Germane Corp Fluid operated motor
US3698841A (en) * 1970-12-21 1972-10-17 Webster Electric Co Inc Hydraulic motor

Cited By (21)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4145167A (en) * 1976-02-17 1979-03-20 Danfoss A/S Gerotor machine with pressure balancing recesses in inner gear
US4357133A (en) * 1978-05-26 1982-11-02 White Hollis Newcomb Jun Rotary gerotor hydraulic device with fluid control passageways through the rotor
US4872819A (en) * 1978-05-26 1989-10-10 White Hollis Newcomb Jun Rotary gerotor hydraulic device with fluid control passageways through the rotor
US4219313A (en) * 1978-07-28 1980-08-26 Trw Inc. Commutator valve construction
US4474544A (en) * 1980-01-18 1984-10-02 White Hollis Newcomb Jun Rotary gerotor hydraulic device with fluid control passageways through the rotor
US4502855A (en) * 1982-11-24 1985-03-05 Danfoss A/S Rotary piston machine with parallel internal axes
US4597725A (en) * 1982-11-24 1986-07-01 Danfoss A/S Rotary piston machine with parallel internal axes
US4981422A (en) * 1987-07-27 1991-01-01 White Hydraulics, Inc. Gerotor device having a valve opening diameter smaller than the drive connection diameter
US4877383A (en) * 1987-08-03 1989-10-31 White Hollis Newcomb Jun Device having a sealed control opening and an orbiting valve
US4859160A (en) * 1987-09-18 1989-08-22 White Hollis Newcomb Jun Cutaway rotor gerotor device
US5215453A (en) * 1991-04-15 1993-06-01 Danfoss A/S Gear wheel assembly for hydraulic purposes, and method assembling the same
US5516268A (en) * 1995-07-25 1996-05-14 Eaton Corporation Valve-in-star motor balancing
EP0756085A3 (en) * 1995-07-25 1998-01-21 Eaton Corporation Gerotor motor and commuting valve
WO2003074874A1 (en) * 2002-03-05 2003-09-12 Sauer-Danfoss Aps Hydraulic machine
US20050180873A1 (en) * 2002-03-05 2005-08-18 Sauer-Danfoss Aps Hydraulic machine
US7963754B2 (en) 2002-03-05 2011-06-21 Sauer-Danfoss Aps Hydraulic machine
US20060067849A1 (en) * 2004-09-28 2006-03-30 Aisin Seiki Kabushiki Kaisha Rotor structure of inscribed gear pump
US20070092392A1 (en) * 2005-10-20 2007-04-26 Aisin Seiki Kabushiki Kaisha Internal gear pump
US20070292295A1 (en) * 2006-06-15 2007-12-20 White Drive Products, Inc. Rotor with cut-outs
US7481633B2 (en) * 2006-06-15 2009-01-27 White Drive Products, Inc. Rotor with cut-outs
US20150050176A1 (en) * 2011-11-24 2015-02-19 Zhengjiang Dali Hydraulic Motor Co., Ltd. Cycloidal Pinwheel Pair with Uniform Contact and One-tooth Difference

Also Published As

Publication number Publication date
DE2240632A1 (de) 1974-03-07
DD106440A6 (enrdf_load_stackoverflow) 1974-06-12
GB1408806A (en) 1975-10-08
JPS5332525B2 (enrdf_load_stackoverflow) 1978-09-08
FR2196678A6 (enrdf_load_stackoverflow) 1974-03-15
JPS4959302A (enrdf_load_stackoverflow) 1974-06-08
IT1059810B (it) 1982-06-21
BE802032R (fr) 1973-11-05
DE2240632C2 (de) 1983-09-01
CH582833A5 (enrdf_load_stackoverflow) 1976-12-15
SE391007B (sv) 1977-01-31

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