EP1053408A1 - Element de machine a crantage hirth - Google Patents

Element de machine a crantage hirth

Info

Publication number
EP1053408A1
EP1053408A1 EP99908876A EP99908876A EP1053408A1 EP 1053408 A1 EP1053408 A1 EP 1053408A1 EP 99908876 A EP99908876 A EP 99908876A EP 99908876 A EP99908876 A EP 99908876A EP 1053408 A1 EP1053408 A1 EP 1053408A1
Authority
EP
European Patent Office
Prior art keywords
toothing
elements
individual
hirth
flank
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP99908876A
Other languages
German (de)
English (en)
Inventor
Hans Betzler
Hans Lindenthal
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Voith Turbo GmbH and Co KG
Original Assignee
Voith Turbo GmbH and Co KG
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
Priority claimed from DE29802374U external-priority patent/DE29802374U1/de
Priority claimed from DE19805676A external-priority patent/DE19805676A1/de
Application filed by Voith Turbo GmbH and Co KG filed Critical Voith Turbo GmbH and Co KG
Publication of EP1053408A1 publication Critical patent/EP1053408A1/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • 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
    • F16D1/00—Couplings for rigidly connecting two coaxial shafts or other movable machine elements
    • F16D1/06—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end
    • F16D1/076—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end by clamping together two faces perpendicular to the axis of rotation, e.g. with bolted flanges
    • 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
    • F16D1/00—Couplings for rigidly connecting two coaxial shafts or other movable machine elements
    • F16D1/02—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for connecting two abutting shafts or the like
    • F16D1/033—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for connecting two abutting shafts or the like by clamping together two faces perpendicular to the axis of rotation, e.g. with bolted flanges

Definitions

  • the invention relates to a Hirth-toothed machine element for positive connection with a second, complementarily toothed machine element.
  • Hirth gears have long been known as construction elements for a variety of different purposes. As a representative reference is made to the Voith company brochure G 749 9.92 1500. The basic idea of the Hirth gearing is to have all geometric lines one
  • a toothed ring which runs in the circumferential direction and has teeth extending in the radial direction with respect to the central axis, is thus created on a machine element for the purpose of torque transmission.
  • Machine elements with complementary Hirth serrations enable the creation of a positive self-centering connection between them, the Hirth serrations being used as such as a space-saving part element with high partial accuracy or as a fixing element with high repeatability.
  • connecting elements are very versatile and are not restricted to specific examples of use.
  • Use in general mechanical engineering is conceivable, for example when connecting high-speed compressors and turbine impellers to the rotor shaft, gear sets or crankshafts.
  • a performance increase can be achieved with the same volume where conventional screw connections, eg. B. flanges, hubs and shafts have reached or exceeded the limit of transmission capacity.
  • a gain in volume and mass can also be achieved with such a connection where the space is already very limited.
  • the assembly designed very easy due to the centering effect, furthermore, components designed in this way are very easily interchangeable.
  • connection of two machine elements with mutually complementary Hirth teeth is usually axially preloaded.
  • means are used in addition to the form-fitting and self-centering connection, which enable axial bracing of the two machine elements to be coupled together.
  • Axial bracing means the generation of bracing with at least one component in the direction parallel to the axis of rotation of the machine elements.
  • Mainly screw connections and tie rods are used as a means. In addition to an additional weight gain, these also require an increased amount of installation space, which corresponds to this in advance
  • the invention is therefore based on the object of further developing a positive connection by means of a Hirth toothing in such a way that the disadvantages mentioned are avoided, in particular that the increased
  • a Hirth toothing or a machine element provided with a Hirth toothing for transmitting torque to another is provided with a complementary Hirth toothing Machine element implemented by realizing a positive connection between the two such that at least one or at least individual toothing elements are asymmetrical, ie have an asymmetrical geometry with respect to the tooth profile.
  • a Hirth toothing is understood to mean a toothing which is preferably used in rotating components and is designed such that the geometric lines of the front toothing are wedge-shaped and bring them together centrally at a point which is on the axis of symmetry or axis of rotation of the machine element is arranged.
  • the gearing itself is one
  • Spline teeth the individual flanks of which can essentially be described by means of one plane.
  • the toothing itself is arranged in the circumferential direction of the rotating component.
  • the individual toothing elements extend in the radial direction with respect to the axis of rotation, the flanks are each aligned in the circumferential direction.
  • Tooth height differs in the radial direction from the axis of rotation, with regard to the height and dimensions of the individual toothing element and the dimension of the toothing.
  • the toothing is designed inclined to the central center or to the axis of rotation.
  • a part that can be compensated for the torque transmission due to the peripheral force from the positive and self-centering connection of the Hirth toothing this part being a function of the number of compensation points, ie the correspondingly designed toothing elements, and / or the geometry of the individual gear elements;
  • the asymmetrical structure is achieved in that a first flank of the individual toothing elements is made steeper than the other second flank.
  • the position of the flanks can be described using the flank angle, which is the one that can be described by the individual flank
  • the second flatter flank of a toothing element takes up an angle of 29 ⁇ 80 °, preferably ⁇ 80 °.
  • a negative flank angle is also conceivable, so that the machine elements get caught in the operating state.
  • the angle of the flanks is understood to mean the angle that lies between the
  • the direction of rotation is such that the surface of the toothing flank with the steeper flank points or is directed in the circumferential direction against the direction of rotation.
  • the steeper flank is designed as a straight flank, ie with an angle of 90 ° with respect to the head line, so that a flank angle of 0 ° is achieved.
  • this embodiment is characterized by a low manufacturing outlay.
  • Gearing in particular the flatter flank, a sliding of the flanks of the intermeshing gears of the two machine parts when a certain predefined axial force is exceeded.
  • Tooth is a tooth base, preferably in a rounded shape, incorporated.
  • the tooth head of the Hirth toothing is preferably designed as a flat surface.
  • individual toothing elements can either be combined to form a single toothing element or a form-fitting connecting element, or, viewed over the circumference, partial areas can be designed entirely free of toothing.
  • the gear elements can have a uniform or different geometry. If gaps are provided or gearing elements combined from several individual elements, it must be taken into account that the counter element must be designed accordingly. There are a number of options for this.
  • a first possibility consists in the mutually complementary design of the gap area and the toothing segment, so that the two machine elements essentially also lie in these areas over larger areas.
  • the toothed elements combined from several toothed elements can be designed with a lower head height than the adjacent toothed elements on the same machine element, so that in this area a flat superimposition of the two machine elements to be coupled with one another is achieved, this area being optimal for the accommodation or Arrangement of connecting elements can be used, or larger spaces remain between the two machine elements.
  • the design, geometry and / or the definition of dimensions of the individual toothing elements can be carried out analogously to other toothing elements in the different design variants; the toothing elements are preferably produced with a uniform geometry and uniform dimensions. Another possibility, however, is to design individual toothing elements differently from one another with regard to their geometry and / or their dimensions.
  • the asymmetrical teeth are preferably designed with regard to their geometry such that flanks aligned in the same direction, the direction being described by the course of the flank plane, each point in one direction with respect to the circumferential direction. With the same orientation of the flanks, the function is determined depending on the direction of rotation. Steeper flanks than first
  • Flanks viewed in the circumferential direction during rotation cause tension.
  • Steeper flanks viewed as the second flank of a toothed element in the circumferential direction when rotating, serve to implement the second function as an overrunning clutch.
  • the individual toothing elements in terms of their geometry and / or dimensions in such a way that both axial force components can be supported in one and in the other direction of rotation of the machine element. This is preferably achieved by considering individual ones in the circumferential direction of the machine element
  • Segments are created which are provided with toothings of different toothing geometries, in particular their flank planes, viewed in the circumferential direction, are oriented opposite to one another. Such an implementation, however, presupposes an increased manufacturing outlay, which is due to the universal
  • the asymmetrical toothing can be manufactured using milling cutters or grinding wheels. Furthermore, it is possible to drop-forge the individual gears by means of shaping, sintering and rolling. In this case, impact hardening can also take place.
  • the functions of torque / speed transmission and the increase in accuracy and repeatability are also optimally fulfilled with the asymmetrically designed Hirth toothing. The stresses can be minimized by appropriately designed surface pressures.
  • the use cases themselves can be designed in many different ways. It is irrelevant in which installation position the machine elements and thus the alignment of the Hirth splines are. Representative as possible application examples are the use in cardan shaft, as a connection and power transmission element for use in nuclear reactors, gyroscopes, e.g. Compressors, fans and in
  • Gear element or the possibility of executing gear arrangements with gap areas depends on the specific application and the loads occurring there and is therefore at the discretion of the responsible specialist.
  • the advantages of a Hirth spline are optimally used, with the additional possibility of considerably reducing the axial forces required for pretensioning the two machine elements to be coupled to one another and thus also the number of means required to apply this pretensioning force for a specific one Direction of rotation can be reduced, and furthermore at the same
  • the same connecting element can be used as a safety clutch.
  • 1a shows a possible embodiment of a Hirth spur toothing designed according to the invention for realizing a form-fitting and self-centering connection between two machine parts to be coupled to one another using one
  • Fig. 1 b illustrates the slope of the individual
  • FIG. 2 illustrates an embodiment with asymmetrical toothing elements designed according to the invention, the toothing having partial areas which are characterized by the combination of individual toothing elements which are adjacent to one another to form a single toothing element;
  • FIG. 3 illustrates a further possible embodiment of a machine element with a Hirth
  • Spur toothing the toothing extending in the circumferential direction having gap regions which are free from toothing elements
  • Fig. 4 illustrates an embodiment of a machine element
  • 5 illustrates an embodiment with a negative flank angle.
  • FIG. 1a illustrates the basic principle of the Hirth spur toothing 1 designed according to the invention in a simplified representation using an exemplary embodiment.
  • Machine element 2 which can be coupled at least indirectly with a drive machine, not shown in detail here, and a second machine element 2 ', which can be coupled at least indirectly with an output, not shown here in detail, are each provided with complementary Hirth stimulating teeth 1 or 1 'designed.
  • the Hirth spur toothing 1 or 1 ' is based on the basic idea that all geometrical lines of a spur toothing are wedge-shaped and converge centrally at one point, here the point G. These individual geometric lines are shown by way of example in FIG. 1a for three gear elements.
  • Gear elements are designated 3, 4 and 5.
  • the corresponding geometric lines are each designated 3 ', 4', 5 'or 3 ", 4" and 5 “or 3'", 4 '"and 5"'. These geometrical lines are defined by the intersection of the theoretically conceived lines on the individual toothing element, which describe and extend the flanks, and the
  • flanks of the individual toothing element - a first flank and a second flank - are each designated 3a, 4a or 5a and 3b, 4b or 5b for the toothing elements 3, 4 or 5, which are designated as examples.
  • the Hirth spur toothing 1 or 1 'designed according to the invention is characterized in that the individual toothing element is designed asymmetrically.
  • the individual flanks here representative flanks 3a or 3b, 4a or 4b and 5a or 5b of the individual toothing elements, here 3, 4 or 5, run at different angles to one another.
  • the individual toothing elements which are arranged at preferably uniform distances from one another over the circumference U of the first or second machine element 2 or 2 ', are constructed with the same geometry.
  • FIG. 1a illustrates this by way of example for the individual toothing elements 9 and 10 using the
  • Points 11 and 12 the distance is labeled a.
  • this also applies to the distances between the individual rectified flanks, for example 3a, 4a, 9a, 10a, 5a or, for example, 3b, 4b, 9b, 10b, 5b of the individual toothing elements which are successive or adjacent in the circumferential direction.
  • the Hirth splines 1 and 1' which are complementary to each other, are brought into engagement with one another.
  • the Hirth spur gearing 1 or 1 'on the individual machine elements 2 or 2' enables a positive fit 12
  • the asymmetrical configuration according to the invention has the effect that a force component which at least partially corresponds to the axial prestressing force for prestressing the two machine elements 2 and 2 'is generated.
  • This geometry is essentially determined by the angle of the flanks.
  • the flanks 3a, 4a and 5a describe a plane E1 3a , E1 4a and E1 5a via their extension b in the radial direction to the central center G, which is simultaneously on the axis of symmetry or axis of rotation of the machine element 2 or 2 ' or E2 3b , E2 4b and E2 5b .
  • the angle of the flanks can then be represented as the angle of these planes E1 and E2 with respect to the line describing the head height Z H of the individual toothing element.
  • Machine element 2 or 2 'plane which can be described by the axis of symmetry S and a line perpendicular to this, runs.
  • the angle of the planes E1 and E2 described by the flanks with the line describing the head height Z H serves to describe the geometry of the toothings.
  • the individual ones 13 are identical to each other.
  • the individual ones 13 are identical to each other.
  • Gear elements which follow one another in the circumferential direction of the machine element 2 are designed with the same geometry.
  • the size of the axial pretensioning forces applied by the geometry of the toothing, which are required for the torque transmission between the two machine elements 2 and 2 ', is a function of
  • the steeper flank of both flanks is preferably designed with a flank angle between 0 degrees and 29 degrees and the angle of the flatter flanks with an angle between 30 and 80 degrees.
  • the size of the angles is preferably selected such that they lie below the self-locking limit. However, it is also conceivable to obtain a negative flank angle for the steeper flank.
  • Means for generating the axial preload between the two machine elements 2 and 2 ' can be dispensed with.
  • the direction of the axial pretensioning forces is described by a parallel to the axis of symmetry or during operation of the axis of rotation of the machine elements 2 or 2 '. Since the use of the means required to generate the axial pretensioning force can be largely reduced, there is no need 14
  • the geometric configuration according to the invention also enables the production of a positive self-centering connection.
  • the Hirth spur toothing as a form-fitting, self-centering connecting element can be used as a space-saving part element with high partial accuracy or as a fixing element with high repeatability.
  • the assembly itself is relatively simple, and individual machine elements are easily interchangeable.
  • FIG. 2 illustrates a further design option for the Hirth spur toothing designed according to the invention.
  • the basic principle and basic structure of the Hirth spur toothing, in particular of the individual toothing elements, essentially corresponds to that described in FIG. 1, which is why the same reference numerals are used for the same elements.
  • the decisive difference is that the individual toothing elements are not designed with the same geometry in the circumferential direction of the machine element 2.
  • the solution according to Figure 2 is characterized in that individual
  • Gear element can be summarized.
  • These preferably have the same angles with respect to their flanks 14a or 15a and 14b or 15b as those of the other toothing elements which are adjacent to one another, but these each form a stop face, here with 16 for the
  • This stop surface 16 or 17 is formed by the top surface of this toothed element 14 or 15, which is widened in the circumferential direction.
  • FIGS. 1 and 2 are preferably used for the form-fitting coupling of two machine elements 2 or 2 'to reduce the axial pretensioning forces during operation in one direction of rotation. This direction of rotation is shown in FIG. 1. In this case, the number of means for applying a 16
  • Spur toothing also offers the possibility of using the two machine elements designed with complementary toothings as safety clutches in the form of a so-called overrunning clutch. This is the case if the use for the purpose of torque transmission in a direction of rotation of the first
  • Machine part 2 takes place contrary to that shown in FIG. 1a.
  • the individual flanks of the two flanks of the two mutually complementary toothings 1 and 1 'provided with one another can slide. The sliding takes place on the flatter one
  • the solution according to the invention can be used as a connecting element in a large number of examples of applications for torque transmission.
  • the specific design ie the design of the geometry and the arrangement on the individual elements to be coupled with one another and the choice of the installation position, are carried out in accordance with the specific application.
  • the possible embodiments shown in FIGS. 1 and 2 only serve to illustrate the basic principle of the mode of operation of one 17
  • FIG. 2 Another possibility of designing a machine element with the Hirth spur toothing designed according to the invention is shown in FIG. It can be seen from this that it is in no way necessary to provide the individual toothing elements with a constant spacing and the same geometry in the circumferential direction of the individual machine element 2.
  • the individual toothing elements form toothing segments according to FIG. 2, although in FIG. 3 no individual toothing elements are combined to form a toothing element, but toothing elements are removed from the toothed ring. This then creates so-called segments which are arranged in the circumferential direction of the machine element and are free of toothing. These are representative of 18, 19, 20 and
  • the toothed segment 19 comprises several individual toothed elements.
  • the geometry of the individual toothing elements, which are arranged between the toothing elements, the toothing segments and the number of toothing segments, is designed according to the specific application requirements of the individual case.
  • FIG. 4 illustrates in a schematically simplified representation using a machine element 2.4 a further embodiment for an asymmetrical Hirth spur toothing designed according to the invention. Only one machine element has been shown, the second is complementary to the first in terms of toothing.
  • both machine elements 2.4 and the second machine element designed with complementary toothing and not shown here comprise areas which can also be referred to as segments 23 or 24 and 25 or 26, which are characterized in that the individual toothing elements differ in their orientation or opposite 18th
  • the segment 25 of the machine element 2.4 comprises the toothing elements 27, 28, 29, 30, 31, the segment 26 the toothing elements 32 to 36.
  • the flanks of the toothing elements 32 to 36 are opposite to those of the toothing elements, at least with regard to the flatter flank 27 to
  • Machine element in particular the machine element on the drive side, here designated 2.4
  • the gap areas are designated here with 37, 38, 39 and 40.
  • flank angle of the steeper flank is preferably not equal to 0 °.
  • the segments formed with oppositely aligned toothing are preferably arranged in the circumferential direction in such a way that they are distributed symmetrically over the circumference.
  • the respective passive toothing elements e.g. 32-36 and the complementary toothing elements on the opposite machine part to be coupled, should be withdrawn (e.g. by milling) so that the oblique flank of the passive toothing elements does not produce any lifting force, while only the
  • Gear elements 27, 28, 29, 30 and 31 and the opposing gear elements are involved in the torque transmission.
  • Another design option is the division of the
  • FIG. 5 illustrates in a schematically simplified representation using a
  • Machine element 2.5 a further embodiment for an asymmetrical Hirth spur toothing designed according to the invention. Only one machine element has been shown, the second is complementary to the first in terms of gearing. Both machine elements 2.5 and the second machine element designed with complementary toothing and not shown here comprise toothing elements, here designated 40, which are characterized in that the individual toothing elements have a negative flank angle with regard to the steeper flank, i.e. the angle simplified representation based on a machine element 2.4, a further embodiment for an asymmetrically designed according to the invention 20th
  • Hirth spur toothing Only one machine element has been shown, the second is complementary to the first in terms of gearing.
  • both machine elements 2.4 and the second machine element designed with complementary toothing and not shown here comprise areas which can also be referred to as segments 23 or 24 and 25 or 26, which are characterized in that the individual toothing elements are different or different with regard to their orientation are oriented in opposite directions.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Gear Transmission (AREA)
  • Gears, Cams (AREA)

Abstract

L'invention concerne un élément de machine à crantage Hirth qui se caractérise en ce que divers éléments de crantage sont formés de façon asymétrique.
EP99908876A 1998-02-12 1999-02-11 Element de machine a crantage hirth Withdrawn EP1053408A1 (fr)

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
DE29802374U 1998-02-12
DE29802374U DE29802374U1 (de) 1998-02-12 1998-02-12 Hirth-verzahntes Maschinenelement
DE19805676 1998-02-12
DE19805676A DE19805676A1 (de) 1998-02-12 1998-02-12 Hirth-verzahntes Maschinenelement
PCT/EP1999/000893 WO1999041513A1 (fr) 1998-02-12 1999-02-11 Element de machine a crantage hirth

Publications (1)

Publication Number Publication Date
EP1053408A1 true EP1053408A1 (fr) 2000-11-22

Family

ID=26043811

Family Applications (1)

Application Number Title Priority Date Filing Date
EP99908876A Withdrawn EP1053408A1 (fr) 1998-02-12 1999-02-11 Element de machine a crantage hirth

Country Status (2)

Country Link
EP (1) EP1053408A1 (fr)
WO (1) WO1999041513A1 (fr)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102005032653B3 (de) 2005-07-13 2006-11-30 Fette Gmbh Verfahren zur Herstellung einer formschlüssigen Verbindung zwischen einem Werkzeugeinsatz und einem Werkzeugträger eines rotierenden Werkzeugs
EP2610188B1 (fr) * 2011-12-30 2017-12-27 Krones AG Agrégat d'étiquetage
DE102012214581A1 (de) * 2012-08-16 2014-02-20 Krones Ag Palettenwelle mit Kunststoffumspritzung
DE102013219958A1 (de) * 2013-10-01 2015-04-02 Voith Patent Gmbh Kupplungshälfte zum drehfesten Anschließen einer Welle
JP6786452B2 (ja) * 2017-07-28 2020-11-18 日立オートモティブシステムズ株式会社 継手装置

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US4431334A (en) * 1982-04-25 1984-02-14 Rockwell International Corporation Power takeoff yoke shielding and engaging means
DE3235796C2 (de) * 1982-09-28 1984-09-27 Festo-Maschinenfabrik Gottlieb Stoll, 7300 Esslingen Anschlag- und Steuerungsvorrichtung für ein bewegbares Maschinenteil
DE3807887A1 (de) * 1988-03-10 1989-09-21 Hertel Ag Werkzeuge Hartstoff Werkzeugwechselhalter
DE3942432C1 (en) * 1989-12-21 1991-05-23 Sgf Sueddeutsche Gelenkscheibenfabrik Gmbh & Co Kg, 8264 Waldkraiburg, De Swivel joint coupling for vehicle drive shaft - includes rubber core with rigid sleeves through which fixing bolts pass
DE19729660C1 (de) * 1997-07-11 1998-08-27 Butz Peter Verwaltung Rückhalte- bzw. Trennvorrichtung für Kraftwagen, mit einer Rückhaltebahn

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See references of WO9941513A1 *

Also Published As

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