WO2008046423A1 - Dispositif de transmission de forces de torsion - Google Patents

Dispositif de transmission de forces de torsion Download PDF

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Publication number
WO2008046423A1
WO2008046423A1 PCT/DK2007/000448 DK2007000448W WO2008046423A1 WO 2008046423 A1 WO2008046423 A1 WO 2008046423A1 DK 2007000448 W DK2007000448 W DK 2007000448W WO 2008046423 A1 WO2008046423 A1 WO 2008046423A1
Authority
WO
WIPO (PCT)
Prior art keywords
arrangement according
positive
arrangement
parts
hydraulic machine
Prior art date
Application number
PCT/DK2007/000448
Other languages
German (de)
English (en)
Inventor
Claus Jesper Johansen
Thomas Kirk SØRENSEN
Jan Schenkel HØGH
Original Assignee
Sauer-Danfoss Aps
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Sauer-Danfoss Aps filed Critical Sauer-Danfoss Aps
Publication of WO2008046423A1 publication Critical patent/WO2008046423A1/fr

Links

Classifications

    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
    • F03C2/00—Rotary-piston engines
    • F03C2/08—Rotary-piston engines of intermeshing-engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing
    • 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
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • 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
    • F04C2/086—Carter
    • 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
    • F16D31/00—Fluid couplings or clutches with pumping sets of the volumetric type, i.e. in the case of liquid passing a predetermined volume per revolution
    • F16D31/04—Fluid couplings or clutches with pumping sets of the volumetric type, i.e. in the case of liquid passing a predetermined volume per revolution using gear-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
    • F04C2230/00—Manufacture
    • F04C2230/60—Assembly methods

Definitions

  • the invention relates to an arrangement for transmitting torsional forces between a first part, which has a substantially planar first contact surface, and a second part, which has a substantially planar second contact surface, against which the first contact surface bears, wherein the two contact surfaces arranged substantially transversely to a torsion axis and rotatably connected to each other.
  • the invention further relates to a hydraulic machine, in particular a gear machine or a rotary piston machine, the positive displacement type, with a previously described arrangement for transmitting torsional forces.
  • German Patent DE 26 14 471 C2 and US Pat. No. 3,289,602 belonging to the same patent family disclose a rotary piston machine with a displacer unit formed from an internally toothed fixed stator and an externally toothed rotor.
  • the displacer unit is housed in a pump housing comprising a pump cover.
  • the pump cover is fastened to the pump housing together with the stator and a control plate by means of screws.
  • the object of the invention is to provide an arrangement according to the preamble of claim 1, which is simple in construction and inexpensive to produce.
  • the object is in an arrangement for transmitting torsional forces between a first part, which has a substantially planar first Ania- ge Chemistry, and a second part, which has a substantially flat second contact surface, against which the first contact surface, wherein the two Arranged contact surfaces substantially transverse to a torsion axis and rotatably connected to each other, characterized solves that the two parts are rotatably connected to each other by form-fitting elements which are received under bias in each case a positive locking element receiving space of the first part and in each case a positive locking element receiving space of the second part.
  • the prestressed positive locking elements serve to transmit torsional forces between the first and the second housing part.
  • the interlocking elements are advantageously dimensioned and designed such that the pretensioning of the interlocking elements is sufficient to transmit the torsional forces without the interlocking elements being deformed.
  • a preferred embodiment of the arrangement is characterized in that the positive-locking elements are formed by spring pins.
  • the spring pins are resiliently biased biased arranged in the associated form-fitting element receiving spaces.
  • the form-fitting element receiving spaces are blind holes or through-holes in the associated parts.
  • a further preferred exemplary embodiment of the arrangement is characterized in that the spring pins each have essentially the shape of a straight circular cylinder jacket with a slot extending in the longitudinal direction.
  • the spring pins are made in one piece.
  • a further preferred embodiment of the arrangement is characterized in that the positive-locking elements are biased in the radial direction.
  • the spring pins have a larger diameter when not installed than in the installed, prestressed state.
  • a further preferred embodiment of the arrangement is characterized in that the positive-locking elements each have a continuous cavity in the axial direction.
  • the cavities extend preferably parallel to the torsion axis.
  • the continuous cavities serve to carry fasteners.
  • a further preferred embodiment of the arrangement is characterized in that the two parts are held by fasteners with their contact surfaces in abutment against each other.
  • the fastening elements are, for example, fastening screws, by means of which the two parts are held together in the axial direction, that is to say parallel to the torsion axis.
  • a further preferred embodiment of the arrangement is characterized in that the fastening element comprise screws.
  • the fastening elements preferably extend through through holes in one of the parts and are screwed into blind holes in the other part.
  • a further preferred exemplary embodiment of the arrangement is characterized in that at least one fastening element extends through a positive-locking element. This has the advantage that only one blind hole and / or through hole in the associated part is required for the fastening element and the associated positive-locking element.
  • a further preferred embodiment of the arrangement is characterized in that the at least one fastening element and the associated positive-locking element are partially arranged in a common through-hole.
  • the through hole serves on the one hand for receiving one end of the associated positive-locking element.
  • the through hole serves to pass through the associated fastening element.
  • a further preferred exemplary embodiment of the arrangement is characterized in that a plurality, in particular all fastening elements extend through in each case one positive-locking element. There- by a stable, space-saving attachment of the parts together.
  • Another preferred exemplary embodiment of the arrangement is characterized in that at least one further part is held in contact with the first or the second part by the fastening elements.
  • a further contact surface is provided on the first or the second part, at which a further contact surface of the further part comes to rest.
  • a further preferred embodiment of the arrangement is characterized in that at least one of the parts in the associated contact surface has at least one recess for a sealing element.
  • the sealing element is used to seal a preferably surrounded by the sealing element recess to the environment.
  • a further preferred embodiment of the arrangement is characterized in that at least two positive locking elements are provided. Due to the at least two positive locking elements, a stable rotationally fixed connection of the two parts is made possible relative to each other.
  • a further preferred embodiment of the arrangement is characterized in that at least three interlocking elements are arranged distributed uniformly in the circumferential direction. This will ensure that the two parts maintain their relative position to each other in transmitting torsional forces.
  • the distribution of the form-locking elements in the circumferential direction does not have to be quite uniform. Due to the number of teeth, the hydraulic machine may have an odd number of screw holes. If fewer pins or positive locking elements are used it is not always possible to distribute them evenly over the circumference.
  • the above object is achieved in a hydraulic machine, in particular a gear machine or a rotary piston machine, the positive displacement type, by a previously described arrangement for transmitting torsional forces.
  • the hydraulic machine serves to provide a torque and a rotational speed at an output shaft.
  • a preferred embodiment of the hydraulic machine is characterized in that the parts of housing parts of the hydraulic machine are formed.
  • the parts are, for example, a housing base and a ring gear of a gear machine, which is also referred to as a stator.
  • a further preferred embodiment of the hydraulic machine is characterized in that one of the housing parts comprises an internally toothed stator.
  • an externally toothed rotor is rotatably arranged in the stationary internally toothed stator.
  • a further preferred embodiment of the hydraulic machine is characterized in that one of the housing parts comprises a fastening flange.
  • the mounting flange is preferably for attaching the hydraulic machine to a functional device, such as a construction machine, which is driven by the hydraulic machine.
  • a further preferred embodiment of the hydraulic machine is characterized in that further housing parts are held by means of the fastening elements on one of the housing parts.
  • the other housing parts are, for example, a control or channel plate or a housing cover.
  • the invention relates to a hydraulic machine used, for example, as a drive motor on individual wheels of a construction machine.
  • the invention is particularly directed to positive displacement hydraulic pumps and motors, preferably to gear machines having five intermeshing tooth elements.
  • the requirements for the manufacturing tolerances can be reduced by the prestressed positive locking elements. At the same time, a better control over the size of free spaces in the parts is made possible.
  • Figure 1 is a perspective view of a hydraulic machine
  • Figure 2 is a front view of the hydraulic machine of Figure 1;
  • Figure 3 is a perspective view of three parts of the hydraulic machine of Figures 1 and 2;
  • Figure 4 shows the hydraulic machine of Figures 1 to 3 in longitudinal section
  • FIG. 5 shows a form-locking element in plan view
  • FIG. 6 shows the positive-locking element from FIG. 5 in a side view
  • Figure 7 is a force-displacement diagram with two different spring characteristics.
  • an arrangement 1 is shown in different views.
  • the hydraulic machine which is also referred to as a gear machine or rotary piston machine.
  • the hydraulic machine which may be designed as a hydraulic pump or hydraulic motor, comprises a housing 2 with two hydraulic connection points 3, 4.
  • the hydraulic connection point 3 is, for example, a pressure connection point, via which the hydraulic machine 1 is pressurized supplied hydraulic medium, such as hydraulic oil, is supplied.
  • the hydraulic medium is discharged via the hydraulic connection point 4, for example.
  • the housing 2 is provided with a mounting flange 5 having a plurality of through holes for passing through fasteners.
  • the mounting flange or mounting flange 5 serves to releasably secure the hydraulic machine 1, for example, to a construction machine.
  • an output shaft 6 projects out of the housing 2.
  • an arrow 8 is indicated that the output shaft 6 outputs a torque.
  • the torque 8 is generated in the hydraulic machine 1, which is also referred to as a hydraulic motor, from hydraulic energy.
  • the hydraulic medium drives displacement elements, such as gears, vanes, pistons, in the housing 2.
  • An arrow 9 indicates that the torque 8 on the output shaft 6 counteracts a torque acting in the opposite direction of the housing 2.
  • the mounting flange 5 is integrally connected to a first housing part 11.
  • the first housing part 11 is a housing base body through which the output shaft 6 extends.
  • a second housing part 12 On the first housing part 11, a second housing part 12, a third housing part 13 and a fourth housing part 14 are attached.
  • the first housing part 11 has a substantially planar contact surface or mounting surface, which in a first mounting plane 21 on a substantially planar contact surface of the second housing part
  • the second housing part 12 has a further substantially planar contact surface on which in a second mounting plane 22, a substantially planar mounting surface or contact surface of the third housing part
  • the third housing part 13 has a further substantially planar contact surface on which a substantially planar contact surface of the fourth housing part 14 rests in a third mounting plane 23.
  • the second housing part 12 is a sprocket with an internal toothing.
  • the third housing part 13 is a Channel plate comprising a plurality of channels through which the hydraulic medium, which is also referred to as a hydraulic medium, from the hydraulic connection points 3, 4 passes to the housing parts 11, 12.
  • the fourth housing part 14 is a housing cover, which is equipped with the hydraulic connection points 3, 4.
  • the three mounting planes 21 to 23 are arranged parallel to each other.
  • the additional mounting planes 22, 23 only have to be sealed against internal hydraulic pressure.
  • the mounting plane 21, which is also referred to as a mounting surface, as well as the mounting planes 22, 23, which are also referred to as mounting surfaces, must also be sealed against the hydraulic pressure.
  • the essentially planar contact surface of the second housing part 12 is designated by 25.
  • the flat Script pool 25 is arranged in the assembled state of the hydraulic machine 1 in the first mounting plane 21.
  • a plurality of recesses is provided in the contact surface 25 .
  • a plurality of rollers 26, 27 serve to form an internal toothing on the second housing part 12.
  • the internal toothing of the second housing part 12, which is also referred to as a ring gear, is in engagement with an external toothing of an inner gear 29.
  • the inner gear 29 is also referred to as a rotor.
  • the ring gear 12 is also referred to as a stator.
  • the stator 12 is, as will be described below, rotatably connected to the first housing part 11.
  • the rotor 29 is coupled to the output shaft 6, for example, by a further toothing.
  • a number of cavities is formed.
  • the volumes of the individual cavities increase and decrease cyclically.
  • the rotor 29 is excited to rotate.
  • 25 through-holes 31, 32 are recessed in the contact surface.
  • the through holes 31, 32 serve, as will be described below, for receiving form-fitting elements and for passing through fastening elements.
  • an arrow 34 the radius of a pitch circle is indicated, on which the through holes 31, 32 are arranged.
  • the force is indicated, which is exerted in the mounted state of the hydraulic machine 1 of the contact surface 25 of the second housing part 12 on the abutting contact surface of the first housing part 11.
  • the associated friction force is indicated.
  • the frictional force acts in the tangential direction and is therefore also called a tangential force.
  • the reaction torque is not transmitted by friction.
  • positive locking elements 41 to 44 are indicated by dashed lines, which serve to transmit the torque or reaction torque between the two housing parts 11, 12.
  • the positive-locking elements 41 to 44 are spring pins.
  • the spring pin 41 is shown alone in different views.
  • the spring pin 41 comprises a circular cylinder jacket-shaped pin body 65, which has a longitudinal slot 66.
  • One end of the spring pin 41 is provided with a chamfer 67.
  • the spring pin 41 is C-shaped.
  • the spring pin 41 has a longitudinally continuous cavity 68.
  • a blind hole 45 for screwing in a fastening screw 51 to 54 is provided in each case.
  • four through holes 46, 47 and 48 are provided in the housing parts 12, 13 respectively.
  • one part of the blind hole 45 one end of the positive locking element 42 is received.
  • the other end of the interlocking element 42 is received in a part of the through hole 46 of the housing part 12.
  • the two ends of the positive-locking element 42 are received under prestress in the associated holes 45, 46.
  • the interlocking elements or spring pins 41 to 44 serve to transmit the reaction torque occurring during operation of the hydraulic machine 1 between the housing parts 11 and 12.
  • a screw 51 to 54 is guided in each case.
  • the screws 51 to 54 each have a shaft 60 whose outside diameter is slightly smaller than the inside diameter of the associated spring pin 41 to 44.
  • the screws 51 to 54 each have a head 61, which rests against the housing cover 14.
  • the shaft 60 is provided at its free end 62 with a thread which is screwed into a complementarily formed thread in the associated blind hole in the housing part 11.
  • FIG. 7 shows in a diagram the spring force F over the spring travel f for different spring characteristics 71, 72.
  • the dashed lines spring characteristic 71 belongs to a solid, non-resilient pin, as it can be used to the two housing parts 11, 12 rotatably connected to each other.
  • the spring characteristic 72 belongs to a resiliently biased and installed in the prestressed spring pin, as it is indicated in Figure 4 with 41 to 44.
  • FIG. 7 shows that the spring pin has the advantage, in comparison with a solid or non-resilient pin, that the prestressed spring pin with the spring characteristic curve 72 causes much less movement of the parts 11, 12. lative to each other as a massive pen.
  • the two housing parts 11, 12 of the hydraulic machine 1 shown in Figure 4 are rotatably connected by a total of nine spring pins together, of which only four are shown.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Hydraulic Motors (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)

Abstract

L'invention concerne un dispositif de transmission de forces de torsion entre une première pièce (11), qui présente une première face d'application sensiblement plane, et une deuxième pièce (12), qui présente une deuxième face d'application (25) sensiblement plane contre laquelle s'applique la première face d'application. Les deux faces d'application sont disposées sensiblement transversalement à un axe de torsion et sont mutuellement assemblées en solidarité de rotation. Afin de fournir un dispositif qui soit de structure simple et de fabrication économique, les deux pièces (11, 12) sont mutuellement assemblées en solidarité de rotation par des éléments d'engagement positif (41, 44) qui sont respectivement reçus sous précontrainte dans à chaque fois un espace récepteur d'élément d'engagement positif de la première pièce (11) et dans à chaque fois un espace récepteur d'élément d'engagement positif de la deuxième pièce (12).
PCT/DK2007/000448 2006-10-18 2007-10-17 Dispositif de transmission de forces de torsion WO2008046423A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE200610050242 DE102006050242A1 (de) 2006-10-18 2006-10-18 Anordnung zum Übertragen von Torsionskräften
DE102006050242.6 2006-10-18

Publications (1)

Publication Number Publication Date
WO2008046423A1 true WO2008046423A1 (fr) 2008-04-24

Family

ID=38861939

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/DK2007/000448 WO2008046423A1 (fr) 2006-10-18 2007-10-17 Dispositif de transmission de forces de torsion

Country Status (2)

Country Link
DE (1) DE102006050242A1 (fr)
WO (1) WO2008046423A1 (fr)

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB687469A (en) * 1950-06-25 1953-02-11 Standard Telephones Cables Ltd Circuit arrangement generating sawtooth current waves
US2968251A (en) * 1953-07-15 1961-01-17 Eaton Mfg Co Internal gear pump
FR1371781A (fr) * 1963-02-27 1964-09-11 Dispositif de liaison mécanique démontable
GB1386857A (en) * 1972-04-24 1975-03-12 Woodling G V Balanced fluid pressure valve means
JPH03229981A (ja) * 1990-02-01 1991-10-11 Kayaba Ind Co Ltd 中空ダウエル
JPH06137279A (ja) * 1992-10-28 1994-05-17 Kayaba Ind Co Ltd ギヤポンプ
JP2004257246A (ja) * 2002-08-09 2004-09-16 Denso Corp 車両用モータ式燃料ポンプ
EP1598556A1 (fr) * 2004-05-17 2005-11-23 Viking Pump, Inc. Pompe multiple à engrenages

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB687469A (en) * 1950-06-25 1953-02-11 Standard Telephones Cables Ltd Circuit arrangement generating sawtooth current waves
US2968251A (en) * 1953-07-15 1961-01-17 Eaton Mfg Co Internal gear pump
FR1371781A (fr) * 1963-02-27 1964-09-11 Dispositif de liaison mécanique démontable
GB1386857A (en) * 1972-04-24 1975-03-12 Woodling G V Balanced fluid pressure valve means
JPH03229981A (ja) * 1990-02-01 1991-10-11 Kayaba Ind Co Ltd 中空ダウエル
JPH06137279A (ja) * 1992-10-28 1994-05-17 Kayaba Ind Co Ltd ギヤポンプ
JP2004257246A (ja) * 2002-08-09 2004-09-16 Denso Corp 車両用モータ式燃料ポンプ
EP1598556A1 (fr) * 2004-05-17 2005-11-23 Viking Pump, Inc. Pompe multiple à engrenages

Also Published As

Publication number Publication date
DE102006050242A1 (de) 2008-04-30

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