US3775031A - Rotary fluid pressure device - Google Patents

Rotary fluid pressure device Download PDF

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Publication number
US3775031A
US3775031A US00262589A US3775031DA US3775031A US 3775031 A US3775031 A US 3775031A US 00262589 A US00262589 A US 00262589A US 3775031D A US3775031D A US 3775031DA US 3775031 A US3775031 A US 3775031A
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chambers
fluid pressure
teeth
machine according
pressure machine
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Expired - Lifetime
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US00262589A
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English (en)
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G Hansen
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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
    • F04C2/082—Details specially related to intermeshing engagement type machines or pumps
    • F04C2/084—Toothed wheels
    • 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

  • the invention relates to fluid pressure motors and pumps of the type having a gerotor displacement mechanism.
  • the rotary type valving for gerotor mechanisms has first and second sets of alternately arranged ports which have sequential fluid communication with ports of stationary passage which are connected to the displacement chambers. Optimum efficiency normally requires that these ports be formed and positioned with great precision.
  • Auxiliary passages associated with the teeth of the gerotor mechanism itself, and which connect adjacent displacement chambers, effects a precise internal distribution of fluid so that only a gross of coarse fluid distribution is required of the valve ports and the fine or delicate distribution needed for optimum efficiency is performed by the auxiliary passages.
  • the invention relates to a fluid-pressure machine such as a rotary hydraulic pump or motor comprising a toothed wheel and a toothed ring which surrounds the toothed wheel, has one more tooth than the wheel and forms displacement chambers therewith; a diversion valve consisting of two parts, one of which is coupled to the toothed elements and contains first control openings which override second control openings in the other valve part; and passages that lead from the second control openings to the displacement chambers.
  • a fluid-pressure machine such as a rotary hydraulic pump or motor comprising a toothed wheel and a toothed ring which surrounds the toothed wheel, has one more tooth than the wheel and forms displacement chambers therewith; a diversion valve consisting of two parts, one of which is coupled to the toothed elements and contains first control openings which override second control openings in the other valve part; and passages that lead from the second control openings to the displacement chambers.
  • the control openings in the diversion valve must be formed with greeat precision.
  • the peripheral length of the control openings and the distances between them in the circumferential direction must be very precise, since otherwise the control cycle is interfered with.
  • one of the toothed elements moves orbitally and it is only able to drive the associated part of the diversion valve through one coupling, for example, a universal joint shaft.
  • play occurs in such a coupling and this can be considerable, particularly in the case of machines which work in both rotary directions. Even if the diversion valve is precision made, this play adversely I affects. the efficiency of the machine.
  • the object of the invention is to provide a fluidpressure machine in which the problems associated with the diversion valve are greatly reduced.
  • this object is achieved by means of auxiliary passages which are associated with one of the toothed elements and which each connects adjacent displacement chambers on each side of the line of symmetry between inlet and outlet chambers, this connection, however, being substantially interrupted by the other toothed element in the zone of the line of symmetry.
  • auxiliary passages together with the other toothed element, these auxiliary passages form a secondary diversion valve.
  • the primary diversion valve is, therefore, required to effect distribution on a rough basis, whereas precision distribution is carried out by the secondary diversion valve.
  • This precision distribution can be achieved without any great difficulty since the auxiliary passages can be precisely shaped and the toothed elements are in any case precision components.
  • the secondary diversion valve achieves balance between adjacent displacement chambers which are incompletely filled or emptied by the primary diversion valve. Such balance is impeded only in the zone of the line of symmetry, that is, between the delivery side and the low pressure or, suction side. It is particularly important that the parts of the secondary diversion valve should be constituted by the toothed elements themselves or by control elements that are associated with the toothed elements. There is then no possibility of troublesome play caused by the coupling occurring in the secondary diversion valve.
  • the distance in a circumferential sense between adjacent first control openings in the (primary) diversion valve is greater than the circumferential length of the second control openings.
  • the greater distance between the first control openings reduces the normal effect of the primary diversion valve; this, however, can be accepted because of the auxiliary passages located downstream.
  • the greater peripheral distances permit play between the first and second part of the diversion vale without a second control opening moving into contact with a false first control opening.
  • the auxiliary passages are provided in a side wall connected to the toothed ring, and they are overridden by the lateraL surface of the toothed wheel.
  • the form of the auxiliary passages and the contour of the toothed ring then determine the function of this secondary diversion valve.
  • the axuilary passages, the side wall, the toothed ring and the second control openings may be stationary.
  • the toothed wheel may execute a rotary and orbital movement and the first control openings a rotary movement.
  • auxiliary passages are formed by tangential grooves each of which is disposed symmetrically in relation to a trough between adjacent teeth of the ring, that is, if they extend along the line connecting the centre points of the crests of adjacent teeth and terminate at a small distance from these centre points.
  • tangential grooves can be formed, for example, by milling with a side-milling cutter.
  • the grooves terminate at a small distance from the centre points of the crests of the teeth, then when the crest of a tooth or the base of a trough between the teeth of the toothed wheel bears against the crest of a tooth of the toothed ring, the grooves are covered in such a way that the connection between adjacent chambers is interrupted.
  • each tangential groove is so selected that when the colume of a given displacement chamber is at its mminimum, its associated groove is substantially completely covered by the tooth wheel. In this way separation of the inlet and outlet sides is achieved. Furthermore, the cross-section of the tangential grooves can be reduced at its ends. In particular, parts of each tangential groove which are of 'reduced cross-section are such that the groove projects into the two chambers adjacent a given chamber when that chamber is at its minimum volume. This minimum volume chamber undergoes a pressure reversal. Fluid is applied from the high pressure side through the flowrestricting point formed at the end of the tangential groove, only small quantities of fluid being necessary so that no sudden increase in pressure occurs when the said chamber is subsequently presented to the pressure Side system.
  • a radial groove extending approximately to the base of a trough between adjacent teeth and the ring, can be connected to each tangential groove. This ensures that a chamber of small volume can also be connected to the adjacent chamber by way of the tangential groove.
  • auxiliary passages can, of course, be of some other shape, for example, they can be formed by a triangle, the base of which corresponds to the tangential groove and the height of which to the radial groove.
  • auxiliary passages are formed in the peripheral face of the toothed wheel and are overridden by the peripheral face of the toothed ring. In this arrangement it is only necessary to provide auxiliary passages in the toothed wheel; all the other components may remain unchanged.
  • each auxiliary passage is expediently provided in a symetrical manner in the two flanks of each toothed of the wheel, sealing faces for cooperation with the toothed ring being left on the crest of the tooth and on the base of the trough between teeth.
  • This auxiliary passages can be rendered ineffective by sealing off at the crest of the tooth and on the base of the gap between the teeth.
  • Each auxiliary passage preferably consists of two grooves at the peripheral edge of the toothed wheel.
  • FIG. 1 is a diagrammatic illustration of a first fluid pressure machine in the position in which the chamber volume is at a minimum
  • FIG. 2 shows the arrangement of FIG. 1 in a position in which the chamber volume is at a maximum
  • FIG. 3 is a partial section on the line 33 of FIG. 1;
  • FIG. 4 is a partial section on the line 4-4 of FIG. 1;
  • FIG. 5 is a schematic illustration of a second fluid pressure machine in a position in which the chamber volume is at a minimum
  • FIG. 6 illustrates the embodiment of FIG. 5 in a position in which the chamber volume is at a maximum
  • FIG. 7 is a partial section on the line 7--7 of FIG. 6.
  • a stationary toothed ring 1 which has seven teeth 2 co-operates with a tooth wheel 3 which has six teeth 4.
  • the centre point M of the toothed wheel executes a circular movement about the centre point M of the toothed ring.
  • the toothed wheel rotates in the direction of the arrow P in the opposite rotary direction and moves through a distance equal to a tooth pitch during one complete circular movement of the centre point M
  • Seven displacement chambers 5, 6, 7, 8, 9, 10 and 11 are formed between the teeth of the toothed ring and the toothed wheel. If it is assumed that the machine of FIG.
  • the toothed chambers 5, 6 and 7 on one side of a line of symmetry S are subjected to the inlet pressure
  • the displacement chambers 8, 9 and 10 on the other side of the line of symmetry S are subjected to the lower outlet pressure
  • the chamber 1 l of minimum volume is a neutral chamber which, at the stage illustrated, is undergoing a reversal of pressure.
  • a diversion valve is shown on the outer circumference of the stationary toothed ring.
  • these diversion valves are offset axially from the toothed elements 1 and 3.
  • the diversion valve consists of a stationary part which is illustrated as being the ring 1 and a rotatable part 13.
  • the part 13 rotates in the same direction and at the same speed as the toothed wheel 3, but its centre point coincides with M and does not, therefore, rotate like the centre point M of the toothed wheel.
  • the coupling between the toothed wheel and the part 13 of the diversion valve can be achieved, for example, by means of a universal joint shaft not illustrated.
  • the valve part 13 has first control openings 14 and 15 to which are alternately applied the higher inlet pressure and the lower outlet pressure and which are therefore marked in the drawings by the symbols and respectively.
  • the first control openings are equal in numer to twice the number of teeth on the toothed wheel 3.
  • the other valve part 1 has second control openings 16 each of which is connected by way of a passage 17 to the trough formed between two adjacent teeth of the ring 1, that is, to a displacement chamber 5 to 11.
  • the control openings 16, which lead to the displacement chambers 5, 6 and 7, are subjected to the higher pressure
  • the second control openings 16, which lead to the displacement chambers 8, 9 and 10 are subjected to the lower pressure.
  • the second control opening 16, connected to the displacement chamber 11, is not connected to any of the first control openings.
  • Tangential grooves 18 and radial grooves 19 are machined, for example, milled, in an end wall 21 arranged adjacent one face of the stationary toothed ring 1. These grooves form auxiliary channels which, together with the circumference of the toothed wheel 3, constitute a secondary diversion valve.
  • Each tangential groove 18 extends symmetrically across a trough formed between adjacent teeth on the ring 1. Each extends along a straight line which interconnects the crests of adjacent teeth 2 and terminates shortly before the centre of each of these crests.
  • the ends 20 are obliquely machined in such a way that the ends of the adjacent tangential grooves 18 run parallel with each other.
  • Each radial groove 19 extends from a tangential groove 18 to the base of the trough formed between adjacent teeth of its associated displacement chamber.
  • the chambers 5, 6 and 7 are interconnected through the auxiliary passages, that is, the tangential grooves 18 and the radial grooves 19, and the chambers 8, 9 and 10 are likewise interconnected by way of the auxiliary passages.
  • the toothed wheel 3 covers the entire tangential groove 18 in the zone of the smallest chamber 11, whereas on the opposite side of the surface between two adjacent tangential grooves 18 is covered.
  • connection between adjacent chambers is interrupted.
  • FIG. 2 where the line of symmetry has moved through and the chamber 11 in which reversal of pressure is taking place now has the greatest volume.
  • the displacement chamber 5, 6 and 7 which are connected to the outlet side are interconnected through the tangential and radial grooves, and
  • FIGS. 1 and 2 show in broken lines the peripheral lengths hitherto required in the upper control openings 14, 15 and 16. Since during reversal of pressure in the displacement chamber 11, the control opening 14 is required to become effective as soon as the control opening 15 has moved away from the control opening 16, the peripheral length of the conventional control openings must be accurately predetermined. Thus, the distance between adjacent first control openings 14 and 15 should be equal to the peripheral length of the second control opening 16. On account of the unavoidable play between the toothed wheel 3 and the valve part 13, it often happened, however, that the valve part 13 lagged behind in the case of a motor, for example. The chamber 11 of minimum volume was then still subjected to the low outlet pressure whereas, for optimum operation, it should have been supplied with the higher inlet pressure.
  • the maximum possible length of all the control openings 14, 15 and 16 can be reduced as represented in solid lines.
  • the reduction in length is distributed uniformly over the first control openings 14 and 15 and the second control openings 16. If, as a result of play, lagging of the valve part 13 now occurs, It will have no important effect on the operation of the machine.
  • the chamber 11 will not immediately be fed by the associated control openings 16, a connection is established for this purpose between the chamber 5 and the chamber 11, through the auxiliary passages 18 and 19, as soon as the line of symmetry 8 has moved slightly from the illustrated position in the clockwise direction. Consequently, very accurate control is achieved. This effect takes place in both directions of rotation of the machine and it occurs when the machine is used as a motor as well as when it operates as a pump.
  • the chamber 11 Independently of a change in volume of this kind, the chamber 11 is gradually brought to the higher inlet pressure through the flow-restricting point of the chamber 5, and very small quantities of fluid suffice for this purpose, so that when the first control opening 14 under higher pressure moves into contact with the second control opening 16 for the chamber 11, no troublesome sudden rise in pressure occurs.
  • auxiliary passages are not formed in the end wall 21, but in the peripheral face of the toothed wheel 3, and they are overridden by the peripheral face of the toothed ring 1.
  • An auxiliary passage 22 and 23 is provided, in a symmem'cal arrangement, in each of the two flanks of each tooth 4, a sealing surface 24 and 25 remaining on each of the sides of a passage, these surfaces co-operating with the toothed ring.
  • sealing faces 24 constitute means for closing the chamber 11, whereas a sealing face 25 seals off the chambers 7 and 8 from each other.
  • sealing faces 25 this time block off the chamber 11 on both sides, whereas a sealing face 24 separates the chambers 7 and 8 from each other.
  • the auxiliary passages 22 and 23 constitute connections between the chambers 5, 6 and 7 on the one hand, and between the chambers 8, 9 and 10 on the other.
  • FIG. 7 shows that the passages 22 only extend along the side edges of the toothed wheel 3.
  • the base of each of the passages 22 and 23 on the mutually facing flanks of adjacent teeth extends along an arcuate path, and the two passages can, therefore, be formed with a mill ing tool in one operation.
  • a fluid pressure machine 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 line of symmetry and contracting chambers on the other side of said line during relative movement between said gears, and end wall fixedly attached to said ring gear and forming fixed wall means for said chambers, valve means comprising a first valve part fixed relative to said ring gear and a second valve part which rotates in unison with said star gear, a first set of fluid ports in said valve first part having fluid connections with said chambers, said valve second part having a second set of ports cooperable with said first ports of said first valve part to continuously route fluid to said expanding chambers and away from said contracting chambers, articulated auxiliary passage means fixed
  • a fluid pressure machine according to claim 1 wherein the spaces between said second ports in the circumferential sense are greater than the spaces between said first ports.
  • a fluid pressure machine according to claim 2 wherein the circumferential dimensions of all of said ports are less than the maximum possible geometric dimensions.
  • a fluid pressure machine according to claim 1 wherein said auxiliary passage means are formed in said wall means and are overridden by one face of said star gear.
  • auxiliary passage means comprise tangentially extending grooves between adjacent teeth of said ring gear with each groove extending approximately along a line between the center points of the crests of adjacent teeth and terminating small distances from said center points.
  • a fluid pressure machine according to claim 5 wherein a radially extending fluid feeding and exhausting groove is connected to each of said tangentially extending grooves.
  • a fluid pressure machine according to claim 5 wherein one of said grooves is substantially covered by one face of said star gear when the associated one of said chambers has its minimum displacement volume.
  • each of said grooves has reduced cross sections at its ends.
  • each said groove extends into adjacent chambers on the opposite sides of one of said chambers which has its minimum displacement volume.
  • a fluid pressure machine according to claim 1 wherein said auxiliary passage means are formed in the teeth of said star gear and cooperate in a valving manner with the teeth of said ring gear.
  • a fluid pressure machine according to claim 10 wherein said auxiliary passages are grooves to opposite sides of each of said gear teeth with the separating surface area of the crests of the star gear teeth and the troughs therebetween being cooperable with said ring gear teeth.
  • a fluid pressure machine comprising said grooves comprise a pair of grooves for the peripheral portion of each said star gear teeth.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Hydraulic Motors (AREA)
US00262589A 1971-05-14 1972-06-14 Rotary fluid pressure device Expired - Lifetime US3775031A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE712124006A DE2124006C3 (de) 1971-05-14 1971-05-14 Rotationskolbenmaschine für Flüssigkeiten mit einem außenverzahnten und einem innenverzahnten Zahnrad

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US3775031A true US3775031A (en) 1973-11-27

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US00262589A Expired - Lifetime US3775031A (en) 1971-05-14 1972-06-14 Rotary fluid pressure device

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US (1) US3775031A (enrdf_load_stackoverflow)
JP (1) JPS5110884B1 (enrdf_load_stackoverflow)
BE (1) BE782856A (enrdf_load_stackoverflow)
CH (1) CH539204A (enrdf_load_stackoverflow)
DD (1) DD96760A5 (enrdf_load_stackoverflow)
DE (1) DE2124006C3 (enrdf_load_stackoverflow)
DK (1) DK129537B (enrdf_load_stackoverflow)
FR (1) FR2137878B1 (enrdf_load_stackoverflow)
GB (1) GB1395817A (enrdf_load_stackoverflow)
IT (1) IT958840B (enrdf_load_stackoverflow)
SE (1) SE381712B (enrdf_load_stackoverflow)

Cited By (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3846051A (en) * 1973-01-03 1974-11-05 Eaton Corp Valving arrangement in a hydraulic device
US3926151A (en) * 1973-12-14 1975-12-16 Kloeckner Humboldt Deutz Ag Rotary piston combustion engine
US4145167A (en) * 1976-02-17 1979-03-20 Danfoss A/S Gerotor machine with pressure balancing recesses in inner gear
US4343600A (en) * 1980-02-04 1982-08-10 Eaton Corporation Fluid pressure operated pump or motor with secondary valve means for minimum and maximum volume chambers
US4502855A (en) * 1982-11-24 1985-03-05 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
US20040062672A1 (en) * 2002-09-26 2004-04-01 Sauer-Danfoss Holding A/S Transition valving by means of non-return valves
US20050180873A1 (en) * 2002-03-05 2005-08-18 Sauer-Danfoss Aps Hydraulic machine
US20060067849A1 (en) * 2004-09-28 2006-03-30 Aisin Seiki Kabushiki Kaisha Rotor structure of inscribed gear pump
US20060067848A1 (en) * 2004-09-28 2006-03-30 Sauer-Danfoss Aps Hydraulic machine
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
US20090160246A1 (en) * 2006-02-02 2009-06-25 Richard Daigre Control component for hydraulic circuit including spring applied-hydraulically released brake

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2240632C2 (de) * 1972-08-18 1983-09-01 Danfoss A/S, 6430 Nordborg Rotationskolbenmaschine für Flüssigkeiten
DE2606172C2 (de) * 1976-02-17 1983-12-22 Danfoss A/S, 6430 Nordborg Rotationskolbenmaschine für Flüssigkeiten
US4391580A (en) 1980-12-08 1983-07-05 Sundstrand Corporation Liquid fuel supply system for an atomization burner nozzle
DE3249829C2 (en) * 1982-11-24 1990-01-18 Danfoss A/S, Nordborg, Dk Parallel and internal axis rotary piston engine
DE3243404C2 (de) * 1982-11-24 1986-07-24 Danfoss A/S, Nordborg Parallel- und innenachsige Kreiskolbenmaschine

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US211769A (en) * 1879-01-28 Improvement in rotary water-meters
US3233524A (en) * 1962-09-05 1966-02-08 Germane Corp Fluid operated motor
US3514234A (en) * 1968-06-10 1970-05-26 Char Lynn Co Fluid operated devices

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US211769A (en) * 1879-01-28 Improvement in rotary water-meters
US3233524A (en) * 1962-09-05 1966-02-08 Germane Corp Fluid operated motor
US3514234A (en) * 1968-06-10 1970-05-26 Char Lynn Co Fluid operated devices

Cited By (20)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3846051A (en) * 1973-01-03 1974-11-05 Eaton Corp Valving arrangement in a hydraulic device
US3926151A (en) * 1973-12-14 1975-12-16 Kloeckner Humboldt Deutz Ag Rotary piston combustion engine
US4145167A (en) * 1976-02-17 1979-03-20 Danfoss A/S Gerotor machine with pressure balancing recesses in inner gear
US4343600A (en) * 1980-02-04 1982-08-10 Eaton Corporation Fluid pressure operated pump or motor with secondary valve means for minimum and maximum volume chambers
US4502855A (en) * 1982-11-24 1985-03-05 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
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
US6884048B2 (en) * 2002-09-26 2005-04-26 Sauer-Danfoss (Nordborg) Transition valving by means of non-return valves
US6887054B2 (en) 2002-09-26 2005-05-03 Sauer-Danfoss Aps Transition valving by means of non-return valves
US20040062672A1 (en) * 2002-09-26 2004-04-01 Sauer-Danfoss Holding A/S Transition valving by means of non-return valves
US20040175283A1 (en) * 2002-09-26 2004-09-09 Sauer-Danfoss Holding A/S Transition valving by means of non-return valves
US7407374B2 (en) * 2004-09-28 2008-08-05 Sauer-Danfoss Aps Hydraulic machine
US20060067849A1 (en) * 2004-09-28 2006-03-30 Aisin Seiki Kabushiki Kaisha Rotor structure of inscribed gear pump
US20060067848A1 (en) * 2004-09-28 2006-03-30 Sauer-Danfoss Aps Hydraulic machine
US20070092392A1 (en) * 2005-10-20 2007-04-26 Aisin Seiki Kabushiki Kaisha Internal gear pump
US20090160246A1 (en) * 2006-02-02 2009-06-25 Richard Daigre Control component for hydraulic circuit including spring applied-hydraulically released brake
US7914084B2 (en) 2006-02-02 2011-03-29 White Drive Products, Inc. Control component for hydraulic circuit including spring applied-hydraulically released brake
US7481633B2 (en) 2006-06-15 2009-01-27 White Drive Products, Inc. Rotor with cut-outs
US20070292295A1 (en) * 2006-06-15 2007-12-20 White Drive Products, Inc. Rotor with cut-outs

Also Published As

Publication number Publication date
DE2124006B2 (de) 1978-06-22
DK129537C (enrdf_load_stackoverflow) 1975-04-21
IT958840B (it) 1973-10-30
DK129537B (da) 1974-10-21
FR2137878B1 (enrdf_load_stackoverflow) 1973-07-13
DE2124006C3 (de) 1979-03-01
FR2137878A1 (enrdf_load_stackoverflow) 1972-12-29
CH539204A (de) 1973-07-15
JPS5110884B1 (enrdf_load_stackoverflow) 1976-04-07
SE381712B (sv) 1975-12-15
DD96760A5 (enrdf_load_stackoverflow) 1973-04-12
BE782856A (fr) 1972-09-01
DE2124006A1 (de) 1972-11-23
GB1395817A (en) 1975-05-29

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