US3288034A - Rotary motor or pump - Google Patents

Rotary motor or pump Download PDF

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Publication number
US3288034A
US3288034A US439511A US43951165A US3288034A US 3288034 A US3288034 A US 3288034A US 439511 A US439511 A US 439511A US 43951165 A US43951165 A US 43951165A US 3288034 A US3288034 A US 3288034A
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Prior art keywords
casing
rotor
axis
commutator
chamber
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US439511A
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Jr Hollis N White
Harvey C White
Hollis N White
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Individual
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Individual
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Priority to US439511A priority Critical patent/US3288034A/en
Priority to DK414665AA priority patent/DK123182B/da
Priority to DE1553275A priority patent/DE1553275C3/de
Priority to SE02073/66A priority patent/SE326415B/xx
Priority to GB52069/68A priority patent/GB1147607A/en
Priority to GB52866/65A priority patent/GB1147606A/en
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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
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/04—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations specially adapted for reversible machines or pumps
    • 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
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T409/00—Gear cutting, milling, or planing
    • Y10T409/30—Milling

Definitions

  • This invention relates to a hydraulic pump or motor, and, more particularly, to a hydraulic pump or motor wherein the rotor portion has a hypocycloidal movement.
  • Another object of the present invention is to provide in a hydraulic device of the internal external gear type wherein one of the members rotates and orbits relative to the other, the provision of driving -a commutator by means of an eccentric pin type connection between the orbiting member and commutator whereby the commutator is driven only in accordance with the orbital movement of the moving member.
  • Another object of the present invention is to provide in a hydraulic device of the internal external gear type wherein one of the members rotates and orbits relative to the other, the novel mounting of a commutator and eccentric drive therefor from the movable member wherein the drive functions efiiciently and does not become an eccentric lock as in prior art devices.
  • Another object of the present invention is to provide in a hydraulic device of the internal external gear type wherein one of the members rotates and orbits relative to the other, an operating member connecting a shaft and the movable member by means of universal joint type connections and an extension of the operating member serves as an eccentric drive member to rotate a commutator in accordance with the orbiting of the movable member.
  • Another object of the present invention is to provide in a hydraulic device of the internal external gear type wherein one of the members rotates and orbits relative to the other and a commutator regulates flow of fluid to and from the device, the provision of connection means between these recited elements and a shaft wherein only torque and no radial or axial loads are transmitted therebetween.
  • Another object of the present invention is to provide in a hydraulic device of the internal external gear type wherein one of the members rotates and orbits relative to the other, the provisions of a commutator which is of a face type valving design as distinguished from a peripheral type and the fluid ports and passages in the device provide for a generally straight through and unobstructed flow of fluid to and from the internal external gear portion of the device.
  • FIGURE 1 is an elevational view, partially in section, of the invention described as a motor
  • FIGURES 2, 3 and 4 are sectional views taken along the lines 22, 3--3 and 4-4, respectively, as applied to FIGURE 1;
  • FIGURE 5 is an elevational view, partially in section, of a modified form of the invention.
  • FIGURE 6 is an elevational view, partially in section, of a modified form of the invention.
  • FIGURE 7 is a view taken generally along the line 77 of FIGURE 6;
  • FIGURE 8 is a view taken generally along the line 88 of FIGURE 6;
  • FIGURE 9 is a view taken generally along the line 9-9 of FIGURE 6;
  • FIGURE 10 is a view taken generally along the line 1010 of FIGURE 6; and 7 FIGURE 11 is a schematic view showing the path of movement of two of the elements of the device shown in FIGURES 6 through 10.
  • the numeral 10 designates generally a first casing, which is seen to be generally cylindrical.
  • the casing 10, as represented in FIGURE 2 has an axis 11 and an interior wall generally designated 12.
  • the interior wall 12 is equipped with a plurality of teeth or high points 13, suitably spaced apart to define a similar number of low points 14.
  • the high points 13 are referred to as gear teeth, and it will be seen from a consideration of FIGURE 2 that these are adapted to cooperate in the usual fashion with the external teeth 15 of a rotor generally designated 16.
  • the rotor has one less tooth 15 than the number of teeth 13, and, in the illustration given, the rotor 16 has six teeth 15, while the stator .portion defined by the first casing 10 has seven teeth 13.
  • the axis 17 of the rotor 16 is seen to be oflset from the axis 11 of the casing 10, so that the movement developed by the rotor 16 is hypocycloidal, -i.e., possessing both rotary and orbit-a1 components.
  • a second casing generally designated 18 is provided.
  • the second casing 18 is suitably secured by bolts (not shown) to a first outer face 19 of the first casing 10.
  • the second casing 18 is cylindrical and, as seen in FIG- URE 3, is equipped with an axially-extending chamber 20 which has an axis 21 coaxial with the axis 11 of the first casing 10.
  • Pressure fluid is introduced into the chamber 20 through a radially-extending flow or inlet port 22 v and pressure fluid is removed from the second casing 18 through a generally axially-extending flow or outlet port 23.
  • the pressure fluid entering the inlet flow port or passage 22 reaches the stator chamber 24 by means of flow passages or ports 25.
  • Pressure fluid exiting from the stator chamber 24 reaches the outlet passage 23 through other flow passages or ports 26.
  • there is one flow passage or port 27 (see FIGURE 3) which is neither supplying nor removing pressure fluid from the stator chamber 24.
  • the commutation of the passages 2527 is achieved by a commutator generally designated 28 and which is seen in FIGURES 1, 3 and 4.
  • An endplate 29, may be employed to confine the commutator 28.
  • the commutator 28 is generally cylindrical in nature'and has an axis coincident with the axis 21 and coaxial with the axis 11.
  • the commutator 28 is equipped with a generally axiallyextending bore 30 which, in FIGURE 3, is seen to be in communication with the passages 26.
  • the commutator 28 is also equipped with a peripheral notched portion 31 which, also in FIGURE 3, exposes the passages 25.
  • the commutator 28 is advantageously supported for rotation within the chamber 20 by means of needle roller bearings 32, and it is seen that the passages 25-27 are arranged to communicate with the chamber 20 a spaced distance inward of the chamber-defining wall 20a. In the illustration given, this is achieved through inclining axially inwardly the passages 25-27, as best seen in FIGURE 1.
  • the rotation of the commutator 28 is achieved through an amplification pin generally designated 33 and which is seen to extend into a portion of the bore 30, the portion in which the pin 33 is received being designated 30a and which is seen to be eccentric to the axis 21.
  • the pin 33 has an intermediate splined portion 34 cooperating with a splined bore 35 provided in the rotor 16, the splined bore 35 being concentrically related to the axis 17 of the rotor 16.
  • the left-hand side (as illustrated) of the casing has secured thereto a third casing generally designated 37.
  • the third casing 37 has an axis 38 coaxial with the axes l1 and 21, and provides a chamber 39 in which an annularly enlarged portion 40 of an output shaft 41 is housed.
  • the annularly enlarged portion 40 has an axial bore 42 splined as at 43 for cooperation with the splined portion 44 provided on the end of the amplification pin 53 opposite the end received in the commutator 28.
  • the annularly enlarged portion 40 is suitably journaled within :he chamber 39 by means of needle bearings 45, and the shaft 41 extends out of an end opening 46 which is suitrbly sealed by means of an O-ring 47.
  • the shaft 41 'otates, in the illustration given, at a speed one-sixth as Fast as that of the commutator 28 and in the opposite diection.
  • the output shaft thus utilizes only the rotational :omponent of the rotor 16, ignoring the orbital com- )onent.
  • the operation of the hydraulic motor utiizes each orbit of the rotor 16 to drive the commutator 28 me revolution.
  • Each sixth turn or orbit of the rotor 16 lrives the output shaft one revolution and in a direction apposite to that of the commutator.
  • f the rotor 16 the orbiting component of the hypocycloi [a1 movement is utilized to drive the commutator 28. .”
  • he rotational component of the hypocycloidal movement f the rotor 16 is lost because the amplification pin has a tniversal-acting cylindrical end portion 33a engaging the ccentric portion 30a of the bore 30 of the commutator 8.
  • the amplification pin 33 does pick up the rbital component of the hypocycloidal movement of the otor 16, and this is amplified by the length of the pin 3 and the angle which it forms with the axis 11.
  • FIGURE 5 an arrangementessentially similar to :tat of FIGURE 1 is seen, wherein the output shaft is gain designated 41, the third casing generally designated 7, the first casing generally designated 10, and the sec- 0nd casing generally designated 118.
  • the output shaft is gain designated 41
  • the third casing generally designated 7
  • the first casing generally designated 10
  • the sec- 0nd casing generally designated 118
  • there is an amplification pin generally designated 33
  • a commutator in FIGURE 5 generally designated by the numeral 128.
  • the rotor again is generally designated 16.
  • the commutator 128 is equipped with an integral, axiallyextending output shaft generally designated 147, and this provides a high speed output, in the illustration given, six times as fast and in the opposite direction from the output shaft 41.
  • the output shaft is on the axis of the commutator 128, a different output passage arrangement is required, and it is seen in FIGURE 5 that the output passage for the pressure fluid extends radially as at 123, the bore of the commutator being annularly enlarged as at 130b for this purpose, as well as having the eccentric portion 130a for the receipt of the amplification pin 33.
  • the pin 33 may take the direct orbit of the rotor 16 as by being arranged at a zero angle to the axis 21, thereby eliminating any amplification.
  • FIGURES 6 through 11 illustrate a still further modification of the invention disclosed herein and this particular embodiment of the invention will be more specifically described as a pump. It will be readily appreciated by those skilled in the art that the teachings of the present invention are as readily adaptable to a pump as to a motor.
  • the particular hydraulic device described at this point namely a pump, includes in combination a casing 50 having wall means which define a bore 51.
  • An internally toothed stator 53 is fixedly secured or mounted in the casing bore and has an axis 54 which is coaxial with the casing axis.
  • an externally toothed rotor 57 which has an axis 58 and one less tooth than the stator 53 and this rotor is adapted to undertake rotational movement and also orbital movement whereby its axis 58 orbits with respect to the axis 54 of the stator.
  • the rotor and stator may be referred to as fluid displacement means. This movement is generally referred to as hypocycloidal movement.
  • the teeth on the stator have been identified by the reference numeral 55 and the teeth on the rotor have been identified by the reference numeral 59.
  • Wall means serve to define a splined bore 60 which extends through the central portion of the rotor and coaxial therewith.
  • Movement of the rotor 57 through the above mentioned rotational and orbital movement relative to the stator creates a plurality of alternately expanding and contracting chambers between the rotor and stator teeth or more specifically the chambers are located between the stator teeth and the expanding and contracting is caused by the movement of the rotor teeth into and out of these spaces.
  • These chambers have been identified by the reference letters A, B, C, D, E, F and G.
  • a closure plate 62 is positioned in the casing bore 51 on the left side of the rotor and stator construction as seen in FIGURE 6 and provides a closure for the above referred to chambers on this side of the rotor and stator.
  • second face of the porting member is positioned adjacent and flush with the first face of a generally cylindrically or annular shaped commutator 70 which is mounted in the casing bore for rotatable movement above an axis coaxial with the stator axis 54.
  • a second face of the commutator 70 is located adjacent an inside wall surface of an end plate 75 held in place by 'bolts 76 which serve to close an end of the casing 50.
  • the end plate 75 is provided with inlet and outlet ports 78 and 79 respectively which extend in a generally axial direction.
  • the porting member 64 is provided with a plurality of circumferentially spaced ports 81, totaling in this embodiment seven in number. The left end of these ports communicate respectively with the chambers A through G and then extend in a generally axial direction to the second face of the porting member.
  • the commutator member is provided with wall means which define input and output passages 83 and 84 so named in this particular instance because of the hereinafter described direction of rotation of the device, it being clearly understood by those skilled in the art that when the direction of rotation is reversed, the function of the input and output passages is likewise reversed.
  • each of these passages also extend in generally an axial direction and it will be noted from viewing FIGURE 8 that each of these passages has a suflicient circumferential and radial extent to encompass or cover more than one of the circumferentially spaced ports 81 at any given time. It will be seen in FIGURE 8 that the output passage 84 is in fluid communication with three of the ports 81 and the input passage 83 is in communication with three of the ports.
  • the commutator which is of the face type as distinguished from the peripheral type, is mounted for rotation by means of a pin member 86 which is fixedly secured to the end plate 75 at its right end as seen in FIGURE 6 and has its left end received within an opening 87 in the commutator 70.
  • the pin member 86 and the opening 87 are located on the axis of the casing and coaxial with the stator axis 54.
  • An input or output shaft 90 which may be referred to in the case of a pump as a drive shaft and in the case of a motor as a driven shaft, is suitably mounted for rotation upon bearings 91 within the casing 50 and has an axis of rotation coaxial with the stator axis.
  • the shaft 90 has a splined recess 93 within its end which resides within the casing and as will be noted the other end extends to the exterior of the casing.
  • An operating or amplifying member 95 is located within the casing and has a splined or toothed portion 96 referred to at times as a third point or portion which functions as a fulcrum and which resides within the splined recess 93 of the shaft 90.
  • the operating member is also provided with a splined or toothed portion 97 referred to at times as a first point or portion which resides within the splined bore 60 of the rotor and this member also extends through the axial opening in the closure plate 62.
  • the connection of the rotor 57 to the shaft 90 by means of the operating member 95 serves to transmit rotative movement between the shaft 90 and the rotor 57 while in effect filtering out the orbital component of the rotor, particularly in th case where the rotor is driving the shaft in the case of a motor. In the case of a pump, while the shaft is rotating the rotor, the rotor is also undergoing orbital movement.
  • the connecting of the operating member by means of the splined portions 96 and 97 provides in effect a universal joint at each of these positions.
  • the operating member functions as a wobble stick.
  • the operating member is provided with an extension 99 referred to at times as a second point or portion which extends as a continuation of the operating member beyond the rotor and resides on the axis of the operating member and as will be noted, is displaced from the axis of the stator or casing a distance greater than the rotor axis 58 is displaced from the stator axis.
  • this extension provides an eccentric drive with respect to the stator axis and this extension serves to amplify this eccentric drive at least with respect to a corresponding portion of the extension at the place where it leaves the rotor.
  • Wall means are provided in the commutator member and define a drive opening 101 within which the end of the extension 99 resides and this connection or eccentric drive serves to rotate the commutator in accordance with the orbital movement of the rotor.
  • the extension 99 must also orbit the stator axis and in going through this movement causes the commutator to rotate about the pin member 86 which rot-atively mounts the same.
  • the extension also rotates in accordance with the rotation of the rotor,
  • the extension merely turns relative to the drive opening 101 since there is no engagement to transmit the rotative movement of the rotor and in effect the rotative movement is rendered ineffective or filtered out.
  • FIGURE 11 is a schematic view (enlarged three times) illustrating the pin member 86 mounting the commutator for rotation along with the extension 99 driving the commutator and showing the extension 99 eccentric throw (e) with respect to the stator axis 54 about which it turns.
  • the drive it is important that the following equation hold true, namely that:
  • R equals the radius of the means (86) rotatably mounting the commutator
  • R equals the radius of the driving means (99)
  • k equals the coefficient of friction for R
  • R and 2 equals the eccentric throw.
  • the operating member 95 including portions 96 and 97 may be referred to as an intermediate shaft and its axis in transmitting movement between shaft 90 and the rotor 57 describes generally the surface of a :one.
  • the chambers A, B, and C are placed in communication with the output passage 84 by means of the ports 81 which are aligned with this part of the commutator (see FIGURE 8) and the input passage 83 of the commutator provides fluid to the chambers D, E, and F by means of the ports 81 which are in communication therewith.
  • the input passage 83 is at all times in communication with the inlet port 78 and the output passage 84 is at all times in communication with the outlet, port 79.
  • the commutator makes one complete rotation upon one complete orbit of the rotor because of the driving connection by means of the exten sion 99 and drive opening 101 and as a result the chambers which are contracting are always connected to the outlet port 79 and the expanding chambers are always connected to the inlet port 78.
  • the present construction also illustrates a construction where there are no radial or axial loads imposed upon the internal external gear set or the commutator, from the shaft, and the design also provides a substantially straight through flow to and from the external internal gear set.
  • a hydraulic device comprising an internally toothed fixedly mounted stator, an externally toothed rotor mounted within said stator and having a lesser number of teeth than said stator, said rotor being capable of rotary movement about its own axis and orbital movement about the stator axis, said rotary and orbital movement of said rotor creating a plurality of alternately expanding and contracting chambers between the teeth on siad rotor and on said stator, a movable commutator for controlling the entrance and exit of fluid from said alternately expanding and contracting chambers, a main shaft rotatably mounted in a position coaxial with said stator, an intermediate shaft having first and second portions, means connecting said first portion of said intermediate shaft to said main shaft and said second portion of said intermediate shaft to said rotor whereby said main shaft and said rotor rotate together and the axis of said intermediate shaft describes It has also been illustrated in the present invention 8: generally the surface of a cone upon movement thereof, and means coupling said rotor and commutator together
  • a hydraulic device comprising a casing, an internally toothed stator fixedly mounted with said casing, an ext ternally toothed rotor mounted within said stator and having a lesser number of teeth than said stator, said rotor being capable of rotary movement about its own axis and orbital movement about the stator axis, said said rotor, and a pin member connected to said rotor for travel therewith in its orbital movement thereby describing an eccentric path with respect to the stator axis, wall means on said commutator, said pin member engaging said wall means on said commutator for rotating said commutator once for each orbit of said rotor.
  • a hydraulic device comprising a casing, an internally toothed stator fixedly mounted within said casing, an externally toothed rotor mounted within said stator and having a lesser number of teeth than said stator, said rotor being capable of rotary movement about its own axis and orbital movement about the stator axis, said rotary and orbital movement of said rotor creating a plurality of alternately expanding and contracting chambers between the teeth on said rotor and on said stator, a rotatable commutator for controlling the entrance and exit of fluid firom said alternately expanding and contracting chambers, a pivot member extending between said commutator and said casing and coaxial with said stator for rotatably mounting said commutator, a shaft coupled to said rotor and responsive only to the rotary movement of said rotor, and a pin member connected to said rotor for travel therewith in its orbital movement thereby describing an eccentric path with respect to the stator axis, wall means on said commutator,
  • R radius of said pin member
  • R radius of said pivot member
  • k coeflicient of friction for pin member and wall means on commutator engagement
  • a hydraulic device comprising a casing, an internally toothed stator fixedly mounted within said casing, an externally toothed rotor mounted within said stator and having a lesser number of teeth than said stator, said rotor being capable of rotary rnovement about its own axis and orbital movement about the stator axis, said rotary and orbital movement of said rotor creating a plurality of alternately expanding and contracting chambers between the teeth on said rotor and on said stator, -a rotatable commutator for controlling the entrance and exit of fluid from said alternately expanding and contracting chambers, a
  • an operating member having first and second portions, said first portion of said operating member being connected to said shaft by a universal joint connection and said second portion of said operating member being connected to said rotor by a universal joint connection, said operating member having an axis which extends at an angle to the stator axis, said operating member having an extension which cooperates with said commutator for rotating said commutator once for each orbit of said rotor, said shaft and rotor being rotatable together.
  • a hydraulic device comprising a casing, an internally toothed stator fixedly mounted within said casing, an externally toothed rotor mounted within said stator and having a lesser number of teeth than said stator, said rotor being capable of rotary movement about its own axis and orbital movement about the stator axis, said rotary and orbital movement of said rotor creating a plurality of alternately expanding and contracting chambers between the teeth on said rotor and on said stator, a rotatable commutator for controlling the entrance and exit of fluid from said alternately expanding and contracting chambers, a pivot member rotatably mounting said commutator and being coaxial with said stator, a shaft coaxial with said stator, an operating member having first and second portions, said first portion of said operating member being connected to said shaft by a universal joint connection and said second portion being connected to said rotor by a universal joint connection, said operating member having an axis which extends at an angle to the stator axis, said operating member having an
  • a hydraulic device comprising a casing, an internally toothed stator fixedly mounted within said casing, an
  • a hydraulic device including in combination a casing having a bore, an internally toothed stator fixedly mounted in said casing bore and having an axis coaxial therewith, an externally toothed rotor having anaxis and one less tooth than said stator and mounted within said stator for rotational movement with respect thereto and orbital movement whereby its axis orbits with respect to said stator axis, movement of said rotor relative to said stator creating a plurality of alternately expanding and contracting chambers between said rotor and stator teeth, a porting member fixedly mounted in said casing bore and having wall means defining a bore therethrough and first and second spaced faces, said first face of said porting member being positioned adjacent said rotor and stator, a commutator member mounted in said casing bore for rotatable movement and having wall means defining first and second spaced faces, said first face of said commutator member being positioned adjacent said second face of said porting member, inlet and outlet ports in said casing, said second face of
  • a hydraulic motor comprising a first casing ,providing an internally toothed, generally cylindrical chamher, a rotor mounted in said chamber and having a lesser number of external teeth for hyp-ocycloidal movement about the first casing chamber axis, said rotor having an axis offset from the first casing chamber axis and an axial splined bore extending therethrough, a second casing secured to said first casing on said one outer side and providing a chamber having a generally cylindrical inner wall defining an axis coaxial with said first casing chamber axis, a hydraulic fluid inlet passage extending generally radially of said second casing chamber and communicating said second casing chamber with the exterior of said second casing for supplying pressure fluid to said motor for actuating said rotor, a hydraulic fluid outlet passage extending generally axially of said second casing and communicating said second casing chamber with the exterior of said second casing for removing pressure fluid from said first casing chamber, said second casing being equipped With a plurality of flow passages
  • a hydraulic device comprising an internally othed member, an externally toothed member mounted ithin said internally toothed member and having a lesser number of teeth than said internally toothed member, at least one of said internally and externally toothed members being capable of rotary movement about its own axis, one of said internally and externally toothed members being capable of orbital movement about the axis of the other of said members, said movement creating a plurality of alternately expanding and contracting chambers between the teeth on said internally and ex ternally toothed members, a movable commutator for controlling the entrance and exit of fluid from said alternately expanding and contracting chambers, an amplifying member having first, second and third portions, said first portion of said amplifying member being operatively connected to the one of said internally and externally toothed members which is capable of orbital movement,
  • said second portion being operatively connected to said movable commutator, and said third portion being fulcrumed to amplify movement of the second portion whereby said commutator moves in response to the orbital movement of the one of said internally and externally toothed members which is capable of orbital movement.
  • the hydraulic device of claim 11 wherein the amplifying member is a wobble stick universally coupled to the fixed axis shaft and to the orbiting toothed member.
  • a hydraulic device comprising, input-output means rotatable on an axis, fluid displacement means having inner and outer parts which rotate and orbit relative to one another around said axis, an amplifying shaft part disposed at an angle with respect to said axis, means coupling said shaft part to one of said inner and outer parts at a first point along said shaft part and which first point orbits through a first orbital path relative to said axis, thereby orbiting said first point on said shaft part relative to said axis in unison with the fluid displacement means, a commutating porting means for said fluid displacement means and coupled to said shaft part at a second point along the length of said shaft part which orbits through a second orbit-a1 path relative to said axis, means fulcrumming said shaft part at a third point spaced from said first point, said second orbital path amplified to be larger than said first orbital path in proportion to the iangularity of the shaft part and the spacing of said points along the length of the shaft part, whereby the com
  • a hydraulic device comprising an internally toothed member, an externally toothed member mounted within said internally toothed member and having a lesser number of teeth, one of said internally and externally toothed members being capable of rotary movement about its own axis and orbital movement about the axis of the other of said members, said rotary and orbital movement creating a plurality of alternately expanding and contracting chambers between the teeth on said members, a movable commutator for controlling the entrance and exit of fluid from said alternately expanding and contracting chambers, a main shaft rotatably mounted in a position coaxial with the other of said internally and externally toothed members, an intermediate shaft having first and second portions, means connecting said first portion of said intermediate shaft to said main shaft and said second portion of said intermediate shaft to said one of said internally and externally toothed members whereby said main shaft and said one of said internally and externally toothed members rotate together and the axis of said intermediate shaft describes generally the surface of a cone upon movement thereof, and means coupling said one of said internally and

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Hydraulic Motors (AREA)
  • Reciprocating Pumps (AREA)
  • Fluid-Pressure Circuits (AREA)
US439511A 1965-02-24 1965-02-24 Rotary motor or pump Expired - Lifetime US3288034A (en)

Priority Applications (6)

Application Number Priority Date Filing Date Title
US439511A US3288034A (en) 1965-02-24 1965-02-24 Rotary motor or pump
DK414665AA DK123182B (da) 1965-02-24 1965-08-13 Hydraulisk motor eller pumpe.
DE1553275A DE1553275C3 (de) 1965-02-24 1965-12-17 Rotationskolbenmaschine für Flüssigkeiten
SE02073/66A SE326415B (GUID-C5D7CC26-194C-43D0-91A1-9AE8C70A9BFF.html) 1965-02-24 1966-02-17
GB52069/68A GB1147607A (en) 1965-02-24 1966-02-24 Improvements relating to Rotary Hydraulic Pumps or Motors
GB52866/65A GB1147606A (en) 1965-02-24 1966-02-24 Improvements relating to Rotary Hydraulic Pumps or Motors

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US439511A US3288034A (en) 1965-02-24 1965-02-24 Rotary motor or pump

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US3288034A true US3288034A (en) 1966-11-29

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US439511A Expired - Lifetime US3288034A (en) 1965-02-24 1965-02-24 Rotary motor or pump

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US (1) US3288034A (GUID-C5D7CC26-194C-43D0-91A1-9AE8C70A9BFF.html)
DE (1) DE1553275C3 (GUID-C5D7CC26-194C-43D0-91A1-9AE8C70A9BFF.html)
DK (1) DK123182B (GUID-C5D7CC26-194C-43D0-91A1-9AE8C70A9BFF.html)
GB (2) GB1147606A (GUID-C5D7CC26-194C-43D0-91A1-9AE8C70A9BFF.html)
SE (1) SE326415B (GUID-C5D7CC26-194C-43D0-91A1-9AE8C70A9BFF.html)

Cited By (24)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3377873A (en) * 1965-12-08 1968-04-16 Char Lynn Co Counterweight or the like for gerotor gear set
US3443378A (en) * 1967-04-04 1969-05-13 Trw Inc Hydrostatic single unit steering system
US3446153A (en) * 1967-07-17 1969-05-27 Wayne B Easton Fluid pressure operated motor or pump
US3452680A (en) * 1967-08-11 1969-07-01 Trw Inc Hydraulic motor-pump assembly
US3452543A (en) * 1967-11-06 1969-07-01 Trw Inc Hydrostatic device
US3531226A (en) * 1969-06-02 1970-09-29 George V Woodling Bearing support means and drive for rotary valve in fluid pressure device
US3591321A (en) * 1969-12-23 1971-07-06 George V Woodling Valving in combination with fluid pressure operating means
US3598509A (en) * 1970-02-03 1971-08-10 Trw Inc Hydraulic device
US3610786A (en) * 1970-03-27 1971-10-05 George V Woodling Valve system means for fluid pressure operating means
US3692440A (en) * 1971-02-08 1972-09-19 George V Woodling Eccentrically disposed male and female spline teeth
US3703343A (en) * 1970-06-10 1972-11-21 George V Woodling Bearing support means and drive for rotary valve in fluid pressure device
US3715175A (en) * 1971-02-24 1973-02-06 G Woodling Rotary valve component means
US3716311A (en) * 1968-07-11 1973-02-13 G Woodling Independent control means for fluid pressure device
US3748067A (en) * 1971-07-19 1973-07-24 G Woodling Fluid pressure device including axially positionable shaft means and rotary valve means
US3853435A (en) * 1972-11-03 1974-12-10 Kayaba Industry Co Ltd Gerotor device with gear drive for commutator valve
US4025243A (en) * 1973-01-05 1977-05-24 Gresen Manufacturing Company Orbital device
US4036031A (en) * 1974-08-02 1977-07-19 Woodling George V Universal connection means in an orbital fluid pressure device
US4368012A (en) * 1979-07-19 1983-01-11 Woodling George V Fluid pressure assembly having a valve disk member with identical flat sides
US5137438A (en) * 1991-04-18 1992-08-11 Trw Inc. Multiple speed fluid motor
US5173043A (en) * 1990-01-29 1992-12-22 White Hydraulics, Inc. Reduced size hydraulic motor
US5797734A (en) * 1996-11-26 1998-08-25 Chrysler Corporation Pump for hot and cold fluids
DE10056975C2 (de) * 2000-11-17 2002-12-05 Sauer Danfoss Holding As Nordb Hydraulische Maschine, insbesondere Pumpe
DE10056973C2 (de) * 2000-11-17 2002-12-05 Sauer Danfoss Holding As Nordb Hydraulische Maschine, insbesondere Motor
US11898560B1 (en) * 2022-07-22 2024-02-13 Perfobore Inc. Working members of a rotary hydraulic or pneumatic machine

Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US211582A (en) * 1879-01-21 Improvement in rotary water-meters
US547180A (en) * 1895-10-01 Water-meter
US1389189A (en) * 1919-06-10 1921-08-30 Feuerheerd Ernest Rotary motor or pump
US2240874A (en) * 1938-09-23 1941-05-06 Dehavilland Aircraft Rotary fluid-pressure machine
US2871831A (en) * 1959-02-03 Internal gear machines
USRE25126E (en) * 1958-11-25 1962-02-20 Controller for fluid pressure operated devices
USRE25291E (en) * 1956-06-08 1962-12-04 Fluid pressure device and valve
US3087436A (en) * 1960-12-02 1963-04-30 Ross Gear And Tool Company Inc Hydraulic pump
US3097609A (en) * 1959-10-23 1963-07-16 Fmc Corp Rag guard for positive displacement pumps
US3139835A (en) * 1962-08-15 1964-07-07 Davey Compressor Co Rotary pump or motor

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH94291A (de) * 1920-11-08 1922-04-17 Herrmann Julius Maschine mit in einem Gehäuse sich abwälzenden Kolben von unrundem und eckigem Querschnitt.
US2989951A (en) * 1959-04-29 1961-06-27 Germane Corp Rotary fluid pressure device
FR1368073A (fr) * 1963-09-05 1964-07-24 Germane Corp Moteur à fluide sous pression

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US211582A (en) * 1879-01-21 Improvement in rotary water-meters
US547180A (en) * 1895-10-01 Water-meter
US2871831A (en) * 1959-02-03 Internal gear machines
US1389189A (en) * 1919-06-10 1921-08-30 Feuerheerd Ernest Rotary motor or pump
US2240874A (en) * 1938-09-23 1941-05-06 Dehavilland Aircraft Rotary fluid-pressure machine
USRE25291E (en) * 1956-06-08 1962-12-04 Fluid pressure device and valve
USRE25126E (en) * 1958-11-25 1962-02-20 Controller for fluid pressure operated devices
US3097609A (en) * 1959-10-23 1963-07-16 Fmc Corp Rag guard for positive displacement pumps
US3087436A (en) * 1960-12-02 1963-04-30 Ross Gear And Tool Company Inc Hydraulic pump
US3139835A (en) * 1962-08-15 1964-07-07 Davey Compressor Co Rotary pump or motor

Cited By (24)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3377873A (en) * 1965-12-08 1968-04-16 Char Lynn Co Counterweight or the like for gerotor gear set
US3443378A (en) * 1967-04-04 1969-05-13 Trw Inc Hydrostatic single unit steering system
US3446153A (en) * 1967-07-17 1969-05-27 Wayne B Easton Fluid pressure operated motor or pump
US3452680A (en) * 1967-08-11 1969-07-01 Trw Inc Hydraulic motor-pump assembly
US3452543A (en) * 1967-11-06 1969-07-01 Trw Inc Hydrostatic device
US3716311A (en) * 1968-07-11 1973-02-13 G Woodling Independent control means for fluid pressure device
US3531226A (en) * 1969-06-02 1970-09-29 George V Woodling Bearing support means and drive for rotary valve in fluid pressure device
US3591321A (en) * 1969-12-23 1971-07-06 George V Woodling Valving in combination with fluid pressure operating means
US3598509A (en) * 1970-02-03 1971-08-10 Trw Inc Hydraulic device
US3610786A (en) * 1970-03-27 1971-10-05 George V Woodling Valve system means for fluid pressure operating means
US3703343A (en) * 1970-06-10 1972-11-21 George V Woodling Bearing support means and drive for rotary valve in fluid pressure device
US3692440A (en) * 1971-02-08 1972-09-19 George V Woodling Eccentrically disposed male and female spline teeth
US3715175A (en) * 1971-02-24 1973-02-06 G Woodling Rotary valve component means
US3748067A (en) * 1971-07-19 1973-07-24 G Woodling Fluid pressure device including axially positionable shaft means and rotary valve means
US3853435A (en) * 1972-11-03 1974-12-10 Kayaba Industry Co Ltd Gerotor device with gear drive for commutator valve
US4025243A (en) * 1973-01-05 1977-05-24 Gresen Manufacturing Company Orbital device
US4036031A (en) * 1974-08-02 1977-07-19 Woodling George V Universal connection means in an orbital fluid pressure device
US4368012A (en) * 1979-07-19 1983-01-11 Woodling George V Fluid pressure assembly having a valve disk member with identical flat sides
US5173043A (en) * 1990-01-29 1992-12-22 White Hydraulics, Inc. Reduced size hydraulic motor
US5137438A (en) * 1991-04-18 1992-08-11 Trw Inc. Multiple speed fluid motor
US5797734A (en) * 1996-11-26 1998-08-25 Chrysler Corporation Pump for hot and cold fluids
DE10056975C2 (de) * 2000-11-17 2002-12-05 Sauer Danfoss Holding As Nordb Hydraulische Maschine, insbesondere Pumpe
DE10056973C2 (de) * 2000-11-17 2002-12-05 Sauer Danfoss Holding As Nordb Hydraulische Maschine, insbesondere Motor
US11898560B1 (en) * 2022-07-22 2024-02-13 Perfobore Inc. Working members of a rotary hydraulic or pneumatic machine

Also Published As

Publication number Publication date
DE1553275C3 (de) 1981-05-07
SE326415B (GUID-C5D7CC26-194C-43D0-91A1-9AE8C70A9BFF.html) 1970-07-20
DE1553275A1 (de) 1970-05-14
GB1147606A (en) 1969-04-02
DE1553275B2 (de) 1980-08-21
DK123182B (da) 1972-05-23
GB1147607A (en) 1969-04-02

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