US3899270A - Drive connection means for a hydraulic device - Google Patents

Drive connection means for a hydraulic device Download PDF

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Publication number
US3899270A
US3899270A US387988A US38798873A US3899270A US 3899270 A US3899270 A US 3899270A US 387988 A US387988 A US 387988A US 38798873 A US38798873 A US 38798873A US 3899270 A US3899270 A US 3899270A
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United States
Prior art keywords
drive shaft
main drive
spline teeth
input
shaft
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US387988A
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English (en)
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Nils Einar Swedberg
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Eaton Corp
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Eaton Corp
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Priority to US387988A priority Critical patent/US3899270A/en
Priority to CA205,954A priority patent/CA1018783A/en
Priority to DE2437688A priority patent/DE2437688C3/de
Priority to FR7427089A priority patent/FR2241018B1/fr
Priority to GB3492074A priority patent/GB1471259A/en
Priority to DK428374A priority patent/DK146697C/da
Priority to IT26249/74A priority patent/IT1019890B/it
Priority to AU72245/74A priority patent/AU487680B2/en
Priority to JP49092695A priority patent/JPS5076608A/ja
Priority to BR6694/74A priority patent/BR7406694D0/pt
Priority to US05/569,504 priority patent/US3973880A/en
Application granted granted Critical
Publication of US3899270A publication Critical patent/US3899270A/en
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
    • B62D—MOTOR VEHICLES; TRAILERS
    • B62D5/00—Power-assisted or power-driven steering
    • B62D5/06—Power-assisted or power-driven steering fluid, i.e. using a pressurised fluid for most or all the force required for steering a vehicle
    • B62D5/09—Power-assisted or power-driven steering fluid, i.e. using a pressurised fluid for most or all the force required for steering a vehicle characterised by means for actuating valves
    • B62D5/093—Telemotor driven by steering wheel movement
    • B62D5/097—Telemotor driven by steering wheel movement gerotor type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
    • F16D3/16—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts
    • F16D3/18—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts the coupling parts (1) having slidably-interengaging teeth
    • F16D3/185—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts the coupling parts (1) having slidably-interengaging teeth radial teeth connecting concentric inner and outer coupling parts

Definitions

  • I ABSTRACT Axial, positioning means are provided in a hydraulic device of the gerotor type to prevent failure of splined drive connections.
  • the drive connections for the device includes a star member of the gerotor set which partakes of hypocycloidal movement and has a straight splined, central opening extending therethrough, a journalled input-output shaft hollowed at one end with straight splined teeth formed therein, and a universal main drive shaft having crowned spline teeth at its end portions which are in splined, driving engagement with the star member and input-output shaft respectively.
  • the positioning means includes an abutment preventing movement of the main drive shaft in a first axial direction and biasing means forcing the drive shaft into Contact with the abutment and thus preventing movement of the shaft in the opposite axial direction.
  • the biasing means comprises a spring assembly.
  • a hydraulic arrangement provides means for biasing the drive shaft.
  • the invention is particularly applicable to hydraulic devices of the gerotor type and will be described with particular reference thereto. However the invention may have broader applications and may be applied to any drive connection which includes a drive shaft having crowned spline teeth at its end portions received in splined engagement with a rotating and orbiting first power member at one end and a rotatable second power member at its other end.
  • Hydraulic devices particularly applicable to this invention are generally characterized by a gerotor set with associated valving whereby an externally toothed star member eccentrically disposed within an internally toothed ring member rotates and orbits in hypocycloidal motion with respect to the ring member.
  • a splined drive arrangement is commonly used to translate the rotational component of the star members movement either to (motor) or from (pump) a journalled inputoutput shaft.
  • the input-output shaft is hollowed at one end with a plurality of spline teeth disposed therein.
  • the star member has a splined central opening extending therethrough.
  • a main drive shaft oftentimes referred to as a wobble or a dogbone shaft, has crowned spline teeth at both its end portions which establish splined drive connections with the input-output shaft at one end and the star member at the opposite end.
  • the splined drive connections are under considerable stress because hydraulic devices of the gerotor type are commonly used in high torque motor applications. Failures resulting from load fractures of worn spline teeth have occurred in service even though the splined connections are of high alloyed, case carburized steel. Investigations of such failures indicate that the geometry of the drive arrangement tends to develop a seating" tooth wear pattern when the device is acting as a motor under load. When the device acts as a pump, such as in dynamic braking, torque direction is reversed, and an axial force is developed which shifts the main drive shaft with respect to the input-output shaft and star member whereby a second wear pattern tends to develop.
  • the main drive shaft has been fixed with reference to the input-output shaft by a snap ring on the main shaft fitting into a groove which may be formed within the input-output shaft for the purpose of preventing total spline disengagement by axial movement of the main shaft.
  • a snap ring on the main shaft fitting into a groove which may be formed within the input-output shaft for the purpose of preventing total spline disengagement by axial movement of the main shaft.
  • Such structure is not believed capable of preventing spline fractures because the groove must necessarily be wider than the ring to permit orbital and rotational movement of the universal shaft in angular relationship to the input-output shaft. This clearance is believed sufficient to upset the wear pattern formed in the spline teeth.
  • gerotor devices coupled to a controller for use in power steering applications have employed springs to balance or position the spool and sleeve mechanism of the controller. It is known to maintain the springs in compression by utilizing one end of the main drive shaft as a spring seat, as shown in US. Pat. No. 3,613,364 to Goff and this necessarily causes the main shaft to be axially positioned.
  • spline fractures of main shafts used in such controllers do not occur because the drive shaft is not under significant load.
  • the springs employed in such controllers which were designed for valve positioning, could adequately function to position a main drive shaft in a gerotor motor application where the main drive shaft is under significant torque loading.
  • it is not possible to manufacture a drive-train arrangement which provides abutments at the drive shaft ends which could axially fix the drive shaft within proper wear limits because of manufacturing tolerances, thermal expansion, etc.
  • a rotary fluid device comprising a known gerotor set and associated known valving means which results in the star member of the gerotor set rotating and orbiting in hypocycloidal motion with respect to the fixed ring member.
  • Drive to or from the star member occurs by a main drive shaft having external, crowned spline teeth at both end portions.
  • One end portion is in splined engagement with internal splines formed in a hollowed end of an axially fixed, rotatable, input-output shaft member.
  • the drive shafts other end portion is in splined engagement with internal splines formed in a central opening extending through the star member.
  • Axial positioning means are provided for maintaining the main drive shaft in fixed axial relation ship with respect to the input-output shaft and star member.
  • the axial positioning means includes abutment means at one end of the universal main drive shaft preventing axial movement of the drive shaft in one direction and biasing means at the other end of the main drive shaft biasing the drive shaft against the abutment means and preventing movement in the opposite axial direction.
  • the biasing means determined as a function of the torque loading on the input-output shaft and the geometry of the drive arrangement, always assures alignment of the spline tooth wear patterns notwithstanding the motor-pump cyclical loadings on the shaft.
  • the abutment means includes a splined valve drive shaft extending from a star member in an opposite direction to that of the main drive shaft.
  • the biasing means includes the input-output shaft having a second bore concentric with the first bore and communicating therewith and a spring disposed in the second bore biasing the main shaft against the valve drive shaft to prevent axial movement of the drive shaft in the opposite direction.
  • the spring is designed to the maximum torque loading of the input-output shaft or alternatively stated, the torque generated by the gerotor set.
  • the abutment meanscould comprise either the wall terminating the end of the first bore in the inputoutput shaft or the valve drive shaft.
  • the positioning means broadly includes plunger means engaging the main drive shaft and opposite the abutment and high pressure passage means to bias the plunger means into engage with the main drive shaft. In this arrangement the biasing force of the positioning means is directly proportional to the torque imposed on the drive-train arrangement.
  • the plunger means includes a first plunger extending a sliding, sealing engagement through a bore in the valve member to bias the main shaft into abutment with the input-output shaft.
  • a first valve cavity under high pressure in the valving means is provided to bias the first plunger into contact with the main shaft when the star member is rotating in one direction.
  • a second plunger adapted to be in contact with the first plunger is slidingly sealed in a bore in a housing which communicates with a second flow cavity formed in the valve member.
  • the second flow cavity is adapted to be in communication with one of the interchangeable inlet-outlet ports in the device and the first cavity is adapted to be in communication with the other inlet-outlet port.
  • FIG. 1 is a longitudinally sectioned view of a rotary fluid device employing one embodiment of the axial drive positioning means of the subject invention
  • FIG. 2 is a longitudinally sectioned view of a rotary fluid device showing a second embodiment of the axial drive positioning means of the subject invention
  • FIG. 3 is a longitudinal view showing the general geometry of the drive-train arrangement of a rotary fluid device or any other mechanical torque transmitting device employing a crowned splined connection;
  • FIG. 4 is a longitudinal view showing internal and external spline engagement for a portion of the drivetrain
  • FIG. 5 is a projected cross sectional view showing spline tceth engagement taken along Line 5-5 of FIG. 4;
  • FIG. 6 is a view showing a developed wear pattern on .the flank of a spline tooth
  • FIG. 7 is a view of the spline tooth wear pattern taken along Line 7-7 of FIG. 6;
  • FIG. 8 is a section view of the wear pattern taken along Line 88 of FIG. 7.
  • FIG. 1 shows a fluid operated motor 10, it being understood that the term motor applied to such fluid operated devices also encompasses the use of such devices as pumps.
  • Motor 10 comprises several sections secured together which include, in their orderfrom front to rear respectively, an end cap 12, a shaft support casing 13, a gear displacement unit or gerotor set 14, a port plate 15 and a valve casing l6.
  • the basic construction and operation of such a motor 10 is known to those skilled in the art and will be better understood than will be explained herein by reference to US. Pat. No. 3,572,983 to H. McDermott.
  • gerotor set 14 shown in FIG. 1 is known in the art and thus will not be described in detail herein.
  • gerotor set 14 comprises an externally toothed star member 20 eccentrically disposed within an internally toothed ring member 21; the eccentricity e of the gerotor set being shown in FIG. 3 as the distance between the ring members centerline which coincides with the longitudinal centerline '22 of the device and the centerline 23 of the star members axis.
  • the ring member 21 has a plurality (N) of equally spaced rollers 24 defining ring teeth which interact with a plurality (N-l of star teeth 25 to define a plurality (N) of volume chambers 26.
  • the outputrnember of the gerotor set shown is the star member and drive from s tar member 20 is achieved by a plurality of straight, involute type splines 27 disposed about a central opening 28 extending therethrough.
  • gerotor set 14 Disposed at one side of gerotor set 14 may be any known type of valving arrangement which sequentially ports fluid under desired pressure to selective volume chambers 26 while emptying other volume chambers to return to achieve a known motion from star member 20. More particularly star member 20 will partake of hypocycloidal movement withrespect to ring member 21 whereby the centerline of the star member will orbit about the centerline of the ring member to define a circular path of radius e in one given direction of rotational movement while rotating a peripheral distance equal to one star tooth in the opposite rotational direction.
  • Such valving arrangements could comprise a known disc valve arrangement whereby a valving member driven at the orbiting speed of the star member produces desired porting or, alternatively, a commutator-type valving arrangement could be used whereby a valve member driven at the rotational speed of the star member achieves desired porting.
  • a commutator-type valving arrangement is illustrated in the embodiments disclosed and includes port plate 15 abutting one end of gerotor set 14 and valve casing section 16 abutting the port plate.
  • port plate 15 Within port plate 15 are a plurality (N) of port plate passages 23, each port plate passage 23 respectively aligned with a corresponding volume chamber 26.
  • valve casing section 16 In valve casing section 16 is a central cavity 29 which communicates with interchangeable inlet and outlet ports 30, 31 respectively.
  • a rotatable valve member 34 shown biased against port plate 15 by a-plurality of known valve seats 35.
  • valve member 34 When valve member 34 is disposed within central cavity 29 a first valve cavity 37 is defined to exist between the outer periphcry of the valve member and the central cavity, and first valve cavity 37 is in fluid communication with outlet port 31. Similarly, a centrally disposed second valve cavity 38 exists at the rearward end of valve member 34, and a second valve cavity 38 is in fluid communication with the inlet port 30. Within valve member 34 is a first plurality (N-l of circumferentially spaced interchangeable inlet valve passages 39 radially aligned with port plate passages 23 and in fluid communication with second valve cavity 38.
  • a second plurality (N-l) of interchangeable outlet valve passages 40 circumferentially spaced between inlet valve passages 39 and radially aligned with port plate passages 23 are in fluid communication with first valve cavity 37.
  • Rotation of valve member 34 to achieve desired porting occurs via a splined valve drive shaft 42 in splined engagement at one end with star member 20 and at its other end with valve member 34 by means of a centrally splined recess 43 formed therein.
  • end cap and shaft support casing sections 12, 13 Disposed at the opposite end of the gerotor set 14 are end cap and shaft support casing sections 12, 13 which together define a cylindrically stepped opening 45 extending therethrough. Extending within cylindrically stepped opening 45 is an input-output shaft 47 journalled with opening 45 by means of a tapered bearing arrangement 48. Input-output shaft 47 is fixed against axial movement by forward and rearward snap rings 49, 50 within grooves formed in shaft 47 which respectively abut the inner races of forward and rearward bearings 51, 52 of bearing arrangement 48.
  • a first bore 54 extends within shaft 47 from the shaft end 55 adjacent the gerotor set. First bore 54 in turn terminates at wall 56, and a second bore 57 in communication with first bore 54 extends further within shaft 47 and is concentric with the first bore. Within first bore 54 are a plurality of involute straight spline teeth 58.
  • a drive connection between input-output shaft 47 and star member 20 is formed by a main universal drive shaft 60 having external, crowned spline teeth of involute configuration 61, 62 disposed about both its end portions which engage spline teeth 58 in input-output shaft 47 and spline teeth 27 in star member 20 respectively.
  • the drive spline positioning means of the subject invention includes a spring 65 disposed within second bore 57, the function of which will be explained hereafter.
  • FIG. 2 a second embodiment of the drive spline positioning means of the subject invention is shown in a motor similar to the motor shown in the FIG. 1 and like numbers designated by a prime will indicate like parts where applicable.
  • Drive positioning means shown in FIG. 2 include a centrally located first bore 67 extending through valve member 34 and in fluid communication at one end with second valve cavity 38' and at its other end with centrally splined recess 43'. Disposed in sliding sealing engagement within first bore 67 is a first plunger 68 having a forward end 69 adapted to contact valve drive shaft 42 and a rearward end 70 disposed within second valve cavity 38.
  • Formed in valve casing 16 is a second bore 72 axially aligned in a general manner with the first bore 67.
  • Second bore 72 communicates at its forward end with sec ond valve cavity 38 and communicates at its rearward end with a passageway 73 which in turn is in fluid communication with first valve cavity 37'.
  • a second plunger 74 Disposed within second bore 72 and in sliding sealing engagement therewith is a second plunger 74 which has a forward end 75 adapted to contact the rearward end 70 of the first plunger 68 and a rearward end 76 which is adapted to be in fluid communication with passageway 73. It is contemplated that the sliding sealing engagement between first and second plungers 68, 74 within their respective bores 67, 72 is achieved by fit tolerances therebetween although O-rings disposed in grooves in either plungers or bores may be used to achieve the sliding, sealing fit desired.
  • spline teeth 27, 58 in star member 20 and input-output shaft 47 are straight and of the involute type having major, minor and pitch diameters respectively.
  • the teeth of main drive shaft 60 are likewise involute but are crowned on the tooth flanks in the cylindrical plane defined by the pitch diameter from the apex 80 or center of each tooth end portion 61, 62. More particularly the spline teeth taper frustoconically from each apex 80 at angles designated A in FIG. 4, into inner 61A, 62A and outer 61B, 62B angled tooth portions for each tooth portion 61, 62 respectively (FIG. 3). It must be understood that tooth flank crowning angle in the cylindrical plane defined by the pitch diameter is a function of angle A but substantially smaller than angle A.
  • centerline 81 of main drive shaft 60 forms a drive angle B with centerline 22 of the input-output shaft which is equal to the drive angle between main drive shafts centerline 81 and star members centerline 23, also defined as angle B.
  • Drive angle B is determined as a function of main drive shaft length and of the eccentricity e of the device and importantly remains constant in any orbit position of the star member.
  • top outer frustoconical portion 62B and 62A of top and bottom teeth of main drive shaft 81 be parallel with star members spline teeths major diameter to insure adequate tooth contact when the proper spline tooth wear'pattern is formed.
  • top inner frusto-conical portion 62A and bottom outer frustoconical portion 62B of the top and bottom drive shaft teeth be similarly aligned with star members spline teeth.
  • angle A is shown equal to angle B.
  • angle C is made slightly larger, about 30 larger, than the angle B or angle A.
  • FIGS. 3 and 4 indicate only the top and bottom relative spline tooth positions.
  • the positions of the remaining spline teeth for top and bottom positions of the star member will be determined by the position of a line YY (shown in FIG. 4 as extending through apex 80 perpendicular to shaft centerline 81) as it rotates through angle B to coincide with line 55 at sline teeth 90 removed from the teeth illustrated in FIG. 4 and then as the line YY rotates through angle B into its bottommost spline contact position.
  • FIG. 5 taken through plane 55 of FIG. 4 which shows relative spline teeth positions in a new or non-worn condition.
  • the crowned spline teeth in FIG. 5 are projected from circular plane YY into plane 55 which thus appears as an elipse.
  • an elipse will contact a circle only at two points and thus only crowned teeth and 102, which are spaced 90 from upper crowned tooth 103 and positioned at the intersection of plane YY with plane 55, are initially loaded in a line contact as shown.
  • Upper spline tooth 103 is thus spaced a distance D between its pitch circle and that of its mating internally splined tooth and a distance E between the flank of spline tooth 103 and the internal spline tooth flank.
  • Distance E is a function of angles B and F which is shown in FIGS. 4 and 5 respectively.
  • Successive crowned teeth leading to teeth 101, 102 have distances proportionately less, which distances are determined as a function of angle B and F.
  • FIG. 6 shows the flank wear pattern 105 developed on an internally splined tooth, it being clear that the wear of the externally splined teeth will be the mirror image of the internal tooth wear pattern.
  • the flank pattern shown in FIG. 6 may be divided into area X on one side of line 77 and represents the outermost tooth contact area of the mating crowned spline tooth 628 which may occur for example in the spline position of spline tooth 102 in the star member as shown in FIG. 5.
  • FIG. 7 which is a section view of the wear pattern taken along line 77 of FIG. 6 and FIG. 8 which is a sectional view of the wear pattern taken along line 88 of FIG. 7 show that the greatest wear occurs at the center 106 of the spline tooth flank along a line which is coplanar with line 55 and that the depth of the wear pattern decreases along a spherical taper from the center point 106 (FIG. 8).
  • Tests have indicated that the above wear patterns will alleviate spline connection failures if the main drive shaft remains axially fixed'with'respect to the internally toothed splines. Tests have also indicated that the wear pattern developed is directly related to the magnitude of angle B which is established as 2 3" in the embodiment shown, and that the tendency of the main shaft to shift relative to the star and input-output shaft is dependent upon the torque placed on the input-output shaft along with the magnitude of angle B.
  • angle A is fixed at 23, and the motor 10 of the subject invention is used to drive a wheel of an off-highway vehicle.
  • the hydraulic device When the wheel is driven, the hydraulic device will function as a motor; the drive resistance will cause the gerotor set to exert a torque on the input-output shaft and the spline teeth will lock into contact which tends to produce the above-described wear pattern.
  • the vehicle operator releases his foot from the accelerator the vehicle will undergo dynamic braking. That is, the wheel will tend to drive the motor as a pump and the braking torque applied to the input-output shaft will be reversed in direction from that applied to the input-output shaft when the device functions as a motor.
  • the braking torque axially shifts the main drive shaft from its initial worn-in position resulting in a highly concentrated loading on a few spline teeth.
  • motor torque is again applied the original established tooth wear pattern is destroyed and a new proper wear pattern will not develop as long as the axial drive shifting takes place.
  • the proper seating wear pattern described above will not develop.
  • a few splines which may now be fatigued will always be subjected to concentrated loads and premature failures will occur.
  • Tests have correlated the torque exerted on inputoutput shaft 47 with an axial force tending to shift the main drive shaft 60 when the torque is released and reversed to the same extent (dynamic braking). For example with angle B at 2-45 min., a motor torque of 1,000 lb.-in. which is reversed to a pump torque of 1,000 lb.-in. will exert an axial shifting force of 75 lbs. on main drive shaft 60 which thus tends to move shaft 60 relative input-output shaft 47 and star member 20.
  • a maximum, rated motor torque of 7,000 lb.in. will result, upon torque reversal, in an axial shift force of approximately 183 lbs. on main drive shaft 60.
  • spring 65 shown in FIG. 1, is designed to exert a minimum precompressed or assembled load of 200 lbs. on main drive shaft 60. While spring is shown as a helical compression spring, it should be apparent that other known springs including resilient blocks of oilresistant, rubber-like material may be substituted therefor. Spring 65 thus biases main drive shaft 60 into contact with valve drive shaft 42 which in turn will abut the end of splines on port plate surface 107. To provide a good seating contact between the ends of the main drive shaft and the valve drive shaft, the ends of the main drive shaft taper in a frustoconical manner from the center of the shaft at an angle slightly larger than angle B and the valve drive shaft angle is similarly sized dependent upon that members drive angle.
  • the fluid inlet pressure of the device provides the biasing means. Assuming port 31' to be connected with fluid'under high pressure to prodduce rotation of star member 20 in a first given direction, high pressure will be communicated from the port 31' to the first valve cavity 37' and from there to passageway 73. Pressure in passageway 73 will then act on rearward end 76 of second plunger 74 to bias the second plunger into contact with rearward end 70 of first plunger 68. First plunger 68 is then biased forwardly into contact with valve drive shaft 42 which in turn forces a frustoconical end of main drive shaft 60 into seating contact with end wall 56 of input-output shaft 47.
  • plungers In the embodiment disclosed, i.e. a drive angle B of 2-45' with a maximum rated force of 200 lbs. the plungers have a diameter of 0.350 inches. Also plunger ends 70-75 may be flared to prevent galling therebetween when plunger 68 rotates relative to plunger 74.
  • the hydraulic positioning arrangement shown in PK]. 2 is believed to illustrate an arrangement that can be easily incorporated at minimum expense into the design of existing motors.
  • a single plunger could replace both plungers 68, 74 shown.
  • Such arrangement would require a second passage also leading to the rear of the single plunger and check valves would have to be employed in both passages.
  • bores 67, 72 would have to be accurately machined in alignment with one another whereas such machining is not critical in the FIG. 2 embodiment.
  • the axial positioning means of the subject invention fixes the main drive shaft so that drive-train geometry can develop a seating-in" wear pattern on the splines which permits all splines to equally share torque loads imposed on the drive-train.
  • a rotary fluid device comprising:
  • gerotor set having an externally toothed member eccentrically disposed within an internally toothed ring member to define a plurality of volume chambers by teeth interaction;
  • valving means for sequentially providing high and low pressure fluid communication to said volume chambers whereby said externally toothed member partakes of hypocycloidal movement with respect to said ring member;
  • said drive connection means for transmitting torque from the rotation of said externally toothed member to an input-output shaft
  • said drive connection means including said input-output shaft having a first bore axially extending therein from an end thereof and straight spline teeth within a portion of said bore, said externally toothed member having a central opening therethrough with straight spline teeth disposed thereabout and a main drive shaft having crowned spline teeth disposed at its end portions in driving engagement with said straight spline teeth in said input-output shaft and said externally toothed member respectively;
  • axial positioning means for maintaining said main drive shaft in an axially fixed position with respect to said input-output shaft and said externally toothed member, said positioning means including abutment means for preventing axial movement of said main drive shaft in a first axial direction and biasing means for preventing movement of said shaft in a second axial direction opposite said first direction, said abutment means including a rotatable valve member oppositely disposed about said externally toothed member from said main drive shaft and a crowned spline valve drive shaft in splined engagement with said straight spline teeth in said externally toothed member, said biasing means exerting a greater axial force on said main drive shaft than axial forces exerted on said main drive shaft by the torque developed in said gerotor set.
  • said biasing means includes spring means within said second bore for biasing said main drive shaft against said abutment means and preventing axial movement of said main drive shaft, said spring means resiliently precompressed to a predetermined force greater than the axial force exerted on said drive connection means by the torque developed in said gerotor set.
  • a rotary fluid device comprising:
  • gerotor set having an externally toothed member eccentrically disposed within an internally toothed ring member to define a plurality of volume chambers by teeth interaction;
  • valving means for sequentially providing high and low pressure fluid communication to said volume chambers whereby said externally toothed member partakes of hypocycloidal movement with respect to said ring member;
  • said drive connection means for transmitting torque from the rotation of said externally toothed member to an input-output shaft
  • said drive connection means including said input-output shaft having a first bore axially extending therein from an end thereof and straight spline teeth within a portion of said bore, said externally toothed member having a central opening therethrough with straight spline teeth disposed thereabout and a main drive shaft having crowned spline teeth disposed at its end portions in driving engagement with said straight spline teeth in said input-output shaft and said externally toothed member respectively;
  • axial positioning means for maintaining said main drive shaft in an axially fixed position with respect to said input-output shaft and said externally toothed member, said positioning means including abutment means for preventing axial movement of said main drive shaft in a first axial direction and biasing means for preventing movement of said shaft in a second axial direction opposite said first direction, said abutment means including a splined valve drive shaft in driving engagement with said valving means and in splined engagement with said I straight spline teeth in said externally toothed member, said valve drive shaft disposed at a fixed angle relative to the center of said valving means, one of said main drive shaft and said valve drive shaft having a conical end, said biasing means exerting a greater axial force on said main drive shaft than axial forces exerted on said main drive shaft by the torque developed in said gerotor set.
  • a rotary device comprising axial positioning means for spline teeth which operates as drive connection means between a rotating and orbiting main drive shaft and an externally toothed member adapted to partake of hypocycloidal movement and between said main drive shaft and a rotatably fixed input-output shaft, said drive connection means including external, crowned spline'teeth disposed about both end portions of said main drive shaft, one end portion of which is in splined driving relation with internal straight spline teeth in a central opening in said externally toothed member and the other end portion of which is in splined driving relation with internal straight spline teeth in a first bore formed in said input-output shaft, said drive connection means subjected to varying bidirectional torque loading and said axial positioning means effective to develop a singular tooth wear pattern between internal and external spline teeth, said axial positioning means comprising:
  • abutment means at one end of said main drive shaft preventing movement of said main drive shaft in a first axial direction, said abutment means including a rotatable valve member disposed on the side of said externally toothed member opposite that from which said main drive shaft extends, a crowned spline valve drive shaft in splined engagement with said straight spline teeth in said externally toothed member and in splined engagement with said valve member, said valve drive shaft disposed at a fixed angle relative to the center of said valve member, one of said main drive shaft and said valve drive shaft having a frusto-conical end disposed within said externally toothed member; b.
  • biasing means at the other end of said main drive shaft forcing said main drive shaft against said abutment means and preventing movement of said main drive shaft in an opposite axial direction, said biasing means maintaining said main drive shaft in a substantially fixed axial position notwithstanding axial forces exerted on said main drive shaft by the magnitude and direction of torque applied to said drive connection means; and c. said main drive shaft assumes a fixed angular relationship with respect to said input-output shaft, determined in part by said hypocycloidal movement 1 of said externally toothed member.
  • said spring means constitutes a spring having a minimum precompressed-load thereon of 200 lbs. when said input-output shaft is subjected to a maximum bidirectional torque of 7,000 lb.-in.
  • a rotary device comprising axial positioning means for spline teeth which operate as drive connection means between a rotating and orbiting main drive shaft and an externally toothed star member adapted to partake of hypocycloidal movement and between said main drive shaft and a rotatably fixed input-output shaft, said drive connection means including external, crowned spline teeth disposed about both end portions of said maindrive shaft, one end portion of which is in splined driving relation with internal straight spline teeth in a central opening in said star member and the other end portion of which is in splined driving relation with internal straight spline teeth in a first bore formed in said input-output shaft, said drive connection means subjected to varying bidirectional torque loading and said positioning means effective to develop a singular tooth wear pattern between internal and external spline teeth, said positioning means comprising:
  • abutment means at one end of said main drive shaft preventing movement of said main drive shaft in a first axial direction
  • biasing means at the other end of said main drive shaft forcing said main drive shaft against said abutment means and preventing movement of said main drive shaft in an opposite axial direction, said biasing means maintaining said main drive shaft in a fixed axial position notwithstanding axial forces exerted on said main drive shaft by the magnitude and torque direction applied to said drive connection means;
  • said input-output shaft having a second bore therein extending from said first bore and concentric with said first bore;
  • said biasing means being defined by spring means within said second bore, said spring means resil-' iently precompressed a predetermined force to exert said biasing force on said main drive shaft.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • Rotary Pumps (AREA)
  • Hydraulic Motors (AREA)
  • Retarders (AREA)
US387988A 1973-08-08 1973-08-13 Drive connection means for a hydraulic device Expired - Lifetime US3899270A (en)

Priority Applications (11)

Application Number Priority Date Filing Date Title
US387988A US3899270A (en) 1973-08-13 1973-08-13 Drive connection means for a hydraulic device
CA205,954A CA1018783A (en) 1973-08-13 1974-07-30 Drive connection means for a hydraulic device
DE2437688A DE2437688C3 (de) 1973-08-13 1974-08-05 Axialstellvorrichtung für eine parallel- und innenachsige Rotationskolbenmaschine
FR7427089A FR2241018B1 (da) 1973-08-13 1974-08-05
GB3492074A GB1471259A (en) 1973-08-08 1974-08-08 Drive connection means suitable for a hydraulic device
IT26249/74A IT1019890B (it) 1973-08-13 1974-08-12 Complesso di connessionee di comando
DK428374A DK146697C (da) 1973-08-13 1974-08-12 Anordning til lejring af en kardanaksel i en tandhjulsmaskine af planettypen
AU72245/74A AU487680B2 (en) 1973-08-13 1974-08-12 Improved drive connection means fora hydraulic device
JP49092695A JPS5076608A (da) 1973-08-13 1974-08-13
BR6694/74A BR7406694D0 (pt) 1973-08-13 1974-08-14 Um dispositivo hidraulico rotativo e respectivos elementos de posicionamento axial das conexoes motrizes
US05/569,504 US3973880A (en) 1973-08-13 1975-04-18 Drive connection means for a hydraulic device

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US387988A US3899270A (en) 1973-08-13 1973-08-13 Drive connection means for a hydraulic device

Related Child Applications (1)

Application Number Title Priority Date Filing Date
US05/569,504 Division US3973880A (en) 1973-08-13 1975-04-18 Drive connection means for a hydraulic device

Publications (1)

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US3899270A true US3899270A (en) 1975-08-12

Family

ID=23532153

Family Applications (1)

Application Number Title Priority Date Filing Date
US387988A Expired - Lifetime US3899270A (en) 1973-08-08 1973-08-13 Drive connection means for a hydraulic device

Country Status (8)

Country Link
US (1) US3899270A (da)
JP (1) JPS5076608A (da)
BR (1) BR7406694D0 (da)
CA (1) CA1018783A (da)
DE (1) DE2437688C3 (da)
DK (1) DK146697C (da)
FR (1) FR2241018B1 (da)
IT (1) IT1019890B (da)

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4069623A (en) * 1975-09-09 1978-01-24 Maxey Van Q Work rest blade for centerless grinder
US4380420A (en) * 1978-10-14 1983-04-19 Rexroth Gmbh Internal gear machine with rotary valve disk
US4457677A (en) * 1981-12-04 1984-07-03 Todd William H High torque, low speed hydraulic motor
US4940401A (en) * 1989-02-14 1990-07-10 White Hydraulics, Inc. Lubrication fluid circulation using a piston valve pump with bi-directional flow
US5820504A (en) * 1996-05-09 1998-10-13 Hawk Corporation Trochoidal tooth gear assemblies for in-line mechanical power transmission, gear reduction and differential drive
US6026700A (en) * 1997-06-19 2000-02-22 Kop-Flex, Inc. Tooth form parameters for ground teeth of gear spindle coupling and method of making the same
US6699024B2 (en) 2001-06-29 2004-03-02 Parker Hannifin Corporation Hydraulic motor
US20050061558A1 (en) * 2003-05-08 2005-03-24 Gino Jobin Tandem wheel assembly and mobile silvicultural apparatus including the same
US20150314347A1 (en) * 2012-12-06 2015-11-05 Mitsubishi-Hitachi Metals Machinery, Inc. Gear spindle and rolling mill provided with same

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3572983A (en) * 1969-11-07 1971-03-30 Germane Corp Fluid-operated motor
US3613364A (en) * 1970-03-06 1971-10-19 Trw Inc Hydrostatic steering system with hydraulic reaction and reaction limiting

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3572983A (en) * 1969-11-07 1971-03-30 Germane Corp Fluid-operated motor
US3613364A (en) * 1970-03-06 1971-10-19 Trw Inc Hydrostatic steering system with hydraulic reaction and reaction limiting

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4069623A (en) * 1975-09-09 1978-01-24 Maxey Van Q Work rest blade for centerless grinder
US4086065A (en) * 1975-09-09 1978-04-25 Maxey Van Q Method of rigidifying work rest blade for centerless grinder
US4380420A (en) * 1978-10-14 1983-04-19 Rexroth Gmbh Internal gear machine with rotary valve disk
US4457677A (en) * 1981-12-04 1984-07-03 Todd William H High torque, low speed hydraulic motor
US4940401A (en) * 1989-02-14 1990-07-10 White Hydraulics, Inc. Lubrication fluid circulation using a piston valve pump with bi-directional flow
US5820504A (en) * 1996-05-09 1998-10-13 Hawk Corporation Trochoidal tooth gear assemblies for in-line mechanical power transmission, gear reduction and differential drive
US6026700A (en) * 1997-06-19 2000-02-22 Kop-Flex, Inc. Tooth form parameters for ground teeth of gear spindle coupling and method of making the same
US6699024B2 (en) 2001-06-29 2004-03-02 Parker Hannifin Corporation Hydraulic motor
US20050061558A1 (en) * 2003-05-08 2005-03-24 Gino Jobin Tandem wheel assembly and mobile silvicultural apparatus including the same
US20150314347A1 (en) * 2012-12-06 2015-11-05 Mitsubishi-Hitachi Metals Machinery, Inc. Gear spindle and rolling mill provided with same
US9879731B2 (en) * 2012-12-06 2018-01-30 Primetals Technologies Japan, Ltd. Gear spindle and rolling mill provided with same

Also Published As

Publication number Publication date
BR7406694D0 (pt) 1975-05-27
AU7224574A (en) 1976-02-12
FR2241018B1 (da) 1978-03-24
DK146697B (da) 1983-12-05
DK146697C (da) 1984-05-14
IT1019890B (it) 1977-11-30
FR2241018A1 (da) 1975-03-14
DK428374A (da) 1975-04-14
DE2437688B2 (de) 1980-12-04
DE2437688A1 (de) 1975-02-27
CA1018783A (en) 1977-10-11
DE2437688C3 (de) 1981-07-16
JPS5076608A (da) 1975-06-23

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