DK155167B

DK155167B - Clamping means for e.g. definite encompassing of a shaft or expansion until definite abutment against in internal circumferential surface

Info

Publication number: DK155167B
Application number: DK221185A
Authority: DK
Inventors: Boerge Martins
Original assignee: Boerge Martins
Priority date: 1983-09-21
Filing date: 1985-05-20
Publication date: 1989-02-20
Also published as: DK221185D0; DK221185A

Description

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Opfindelsen angår et ringformet spændeelement til f.eks. fast omslutning af en aksel eller udspiling til fast anlæg mod en indvendig omkredsflade og med mindst et spændeelement, der har en rundtgående længde, der er foranderlig ved indbyrdes ak-5 sialforskydning i modsatte retninger ud fra elementets ubelastede stilling af på elementets to modstående radialsider jævnt fordelte elementdele.The invention relates to an annular clamping element for e.g. fixed enclosure of a shaft or flush for fixed abutment against an inner circumferential surface and with at least one clamping element having a circumferential length which is variable by axial displacement in opposite directions from the unloaded position of the element on the two opposite radial sides evenly distributed element parts.

Et spændeelement af denne art kendes f.eks. fra russisk patentskrift nr. 826.118. Det heri omhanlede spændeelement består af en flad, forholdsvis tynd fjederring, der jævnt fordelt skiftevis på den ene og den anden sideflade bærer fremspringende dele, og som er bestemt til at indskydes mellem en endeflade på et på en aksel indskudt organ og en vederlagsring, som kan presses aksialt ind mod den nævnte endeflade.A clamping member of this kind is known e.g. from Russian Patent Specification No. 826,118. The clamping element herein embodied consists of a flat, relatively thin spring ring, which is evenly distributed alternately on one and the other side surfaces, carrying projecting parts and which is intended to be inserted between an end surface of a member inserted on a shaft and a compensation ring which can be pressed axially into said end surface.

1515

Ved en sådan indpresning af vederlagsringen, vil fjederringens fremspringende dele blive presset aksialt i modsatte retninger, hvorved ringen gives en siksak-form, der medfører, at dens rundtgående længde og dermed såvel dens inderdiameter som dens yderdiameter formindskes, 20 så at den bringes til at klemme om akslen. Til opnåelse af en tilstrækkelig stor diameterformindskelse kræves der imidlertid, selv om der kun tilstræbes en diameterreduktion på en brøkdel af en mm, en forholdsvis stor deformation af fjederringen på mange gange dennes tykkelse, idet de ved deformationen dannede i forhold til aksialplaner 2^ skråtforløbende ringpartier skal danne en vinkel med aksialplanerne på mellem 10 og 15°. En så kraftig deformation stiller imidlertid store krav til fjederringsmaterialet, idet blivende deformationer bør undgås, såfremt de opnåede radiale tryk ind mod akslen skal opretholdes.In such a pressing of the recoil ring, the protruding parts of the spring ring will be axially pressed in opposite directions, thereby giving the ring a zig-zag shape which causes its circumferential length and thus both its inner diameter and its outer diameter to be reduced. clamp around the shaft. However, to achieve a sufficiently large diameter reduction, although a diameter reduction of only a fraction of a mm is sought, a relatively large deformation of the spring ring of many times its thickness is required, forming during the deformation relative to axial planes 2 ^ inclined annular portions. must form an angle with the axial planes between 10 and 15 °. Such a strong deformation, however, places great demands on the spring ring material, since permanent deformations should be avoided if the radial pressures obtained towards the shaft are to be maintained.

Ringen er derfor forholdsvis tynd, men dette medfører igen, at det er begrænset, hvor store radiale tryk ind mod akslen, der kan opnås, når de ikke skal frembringe trykkene igen reducerende elastiske deformationer af selve materialet. Et sådant spændeelement er derfor kun egnet til småmaskinerier, hvori der kun skal overføres mindre drejningsmomenter .The ring is therefore relatively thin, but this, in turn, limits the amount of radial pressure towards the shaft that can be obtained when they do not have to produce the pressures again reducing elastic deformations of the material itself. Such a clamping element is therefore only suitable for small machines in which only minor torques are to be transmitted.

3535

For at undgå de ovennævnte ulemper er det ringformede spændeelement ifølge opfindelsen særegent ved, at det har to sæt ved elementets i aksialretningen vendende to modstående sider skiftevis liggende sektioner, primære og sekundære sektioner,In order to avoid the above disadvantages, the annular clamping element according to the invention is peculiar in that it has two sets of two opposite sides of the element facing in the axial direction, alternating sections, primary and secondary sections,

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2 der hver for sig er forbundet med de to hosliggende sektioner gennem i forhold til aks i alretni ngen skråtstillede ringpartier, der danner en vinkel på mellem 15° og 60°, fortrinsvis mellem 20° og 45°, med radiale planer, og hvis hældning er for- g anderlig ved tvangsmæssig aksialforskydning af de to sektionssæt relativt i forhold til hinanden. Som følge af ringpartiernes skråstilling i forhold til aksialretningen vil, blot vinklen med aksialretningen er større end f.eks. 15°, fortrinsvis 20-45°, selv en forholdsvis ringe indbyrdes aksialforskydning 10 mellem sektionerne fremkalde en relativ stor diameterændring af spændeelementets indre såvel som ydre omkreds. Endvidere er det muligt at opnå såvel en diameterformindskelse, f.eks. til brug for elementets fastspænding på en aksel, som en diameterforøgelse, f.eks. til brug for elementets indspænding i en 15 navboring, idet en di ameterreduktion opnås, hvis sektionerne trækkes i modsatte retninger, og en diameterforøgelse, hvis de presses i retning mod hverandre. De små nødvendige elementdeformationer medfører desuden, at der kun skal stilles små krav til det anvendte materiales eftergivenhed, hvorfor elementerne 20 kan gives en forholdsvis stor aksial udstrækning og/eller fremstilles af forholdsvis svært plademateriale, så at der ved deformeringen kan frembringes nok så store radiale anlægstryk mellem elementet og en aksel eller en omsluttende omkredsflade, hvilket igen medfører, at elementet kan anvendes, selv når 2 5 der er tale om overførsel af høje drejningsmomenter. Endvidere kan til elementet anvendes så at sige et hvilket som helst fast materiale, derunder såvel træ som støbejern.2, which are individually connected to the two adjacent sections through inclined annular portions, which form an angle of between 15 ° and 60 °, preferably between 20 ° and 45 °, with radial planes, and whose inclination is different in the case of forced axial displacement of the two section sets relative to each other. Due to the inclination of the ring portions with respect to the axial direction, the angle of the axial direction is greater than, e.g. 15 °, preferably 20-45 °, even a relatively small axial displacement 10 between the sections causes a relatively large diameter change of the inner as well as outer circumference of the clamping member. Furthermore, it is possible to obtain both a diameter reduction, e.g. for use in clamping the element on a shaft, such as a diameter increase, e.g. for use of the element clamping in a hub bore, obtaining a di-ameter reduction if the sections are pulled in opposite directions, and a diameter increase if pressed in a direction toward each other. Furthermore, the small necessary element deformations mean that only small demands have to be placed on the yield of the material used, so that the elements 20 can be given a relatively large axial extent and / or made of relatively difficult sheet material, so that when the deformation can be produced, sufficiently large radial abutment pressure between the element and a shaft or enclosing circumferential surface, which in turn allows the element to be used even when high torque transmission is involved. Furthermore, to the element can be used, so to speak, any solid material, including both wood and cast iron.

En yderligere fordel ved spændeelementet ifølge opfindelsen ligger der-i, at det kan gives en forholdsvis ringe tykkelse og derved en i forhold til midteråbningens diameter ringe yderdiameter. Spændeelementet er derfor velegnet til at tjene som supplement til de spændeelementer, som er beskrevet f.eks. i det internationale offentliggørelsesskrift WO 82/00325. Også ved det heri omhandlede spændeelement frembringes en ligeledes, men i modsætning til spændeelementerne bestående af en enkelt med en aksial opslidsning forsynet spændebøsning med konisk inder- og/eller yderside, eller af to sådanne i hinanden konisk indgribende bøsninger, en nøjagtigt koncentrisk fastspænding på en aksel, 3A further advantage of the clamping element according to the invention lies in the fact that it can be given a relatively small thickness and thereby a small outer diameter relative to the diameter of the center opening. The clamping element is therefore well suited to serve as a supplement to the clamping elements described e.g. in International Publication No. WO 82/00325. Also provided by the clamping element herein, a similar, but in contrast to the clamping elements consisting of a single axially slotted clamping sleeve with conical inner and / or outer sides, or of two such conically engaging bushings, provides an exact concentric clamping on a shaft, 3

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ved en aksial sammenpresning af skiver med en keglestubformet del, hvorved skivens inderdiameter reduceres, og dens yderdiameter forøges.by axial compression of discs with a cone-shaped part, thereby reducing the inner diameter of the disc and increasing its outer diameter.

Disse spændeelementer har imidlertid ofte en i forhold til inderdiame-teren relativt stor yderdiameter, der i visse tilfælde kan forhindre 5 dets anvendelse, medens man i sådanne tilfælde med fordel kan anvende et spændeelement ifølge opfindelsen.However, these clamping members often have a relatively large outer diameter relative to the inner diameter, which in certain cases can prevent its use, while in such cases a clamping member according to the invention can be used advantageously.

En ikke uvæsentlig videre fordel ved et spændeelement ifølge opfindelsen ligger deri, at det, som foran nævnt, kan bringes til såvel at ud-10 vide sig som at trække sig sammen. Dette medfører f.eks., at et spændeelement med et i forhold til en aksel ringe hulovermål, farts kan bringes til at udvide sig, så at det alligevel let kan indskydes over en aksel, for derefter ved modsat påvirkning af sektionerne at bringes til at klemme om akslen med stor kraft. Dette forhold kan være af 15 væsentlig betydning i praksis. En tilsvarende virkning har hidtil ikke kunnet opnås ved spændeelementer til brug ved fastgørelse af et organ på en aksel.A not insignificant further advantage of a clamping element according to the invention lies in the fact that, as mentioned above, it can be caused to expand as well as to contract. This means, for example, that a clamping element with a small hollow dimensions relative to a shaft can be caused to expand far, so that it can still easily be inserted over a shaft, and then caused by opposite influence of the sections to clamp the shaft with great force. This relationship can be of significant importance in practice. To date, a similar effect has not been achieved by clamping elements for use in attaching a member to a shaft.

Udformningen kan endvidere være som angivet i krav, hvorved der kan 20 sikre en over hele elementets aksiale længde ensartet påvirkning af ringpartierne og dermed en ensartet diameterreduktion (eller -forøgelse) over hele elementets længde.Furthermore, the design can be as claimed in claim, whereby a uniform influence over the annular portions of the entire element can be ensured, and thus a uniform diameter reduction (or increase) over the entire length of the element.

Desuden kan med fordel udformningen være som angivet i krav 3, så at en 25 i forvejene eksisterende plan radialflade på et med spændeelementet samarbejdende andet element kan anvendes som vederlag for spændeelementet under dettes deformering.In addition, the configuration may advantageously be as claimed in claim 3, so that a pre-existing plane radial surface of a second element cooperating with the clamping element can be used as consideration for the clamping element during its deformation.

Udformningen kan imidlertid også ofte hensigtsmæssigt være som angivet 30 i krav 4, så at samtlige sektioner kan have en endeflade beliggende i samme radialplan, hvilket ofte kan være en fremstillingsmæssig fordel.However, the design can also often be conveniently as set out in claim 4, so that all sections may have an end surface located in the same radial plane, which can often be a manufacturing advantage.

I sidstnævnte tilfælde kan udformningen endvidere være som angivet i krav 5, så at ét og samme vederlag kan anvendes såvel til udvidelse 35 som til indsnævnring af spændeelementet, blandt andet til brug i det foran omtalte tilfælde, hvor et spændeelement, der har ringe tolerance, 4In the latter case, the design may further be as set out in claim 5, so that one and the same consideration can be used for both extension 35 and for narrowing the clamping element, inter alia for use in the aforementioned case where a clamping member having low tolerance is used. 4

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med sikkerhed let skal kunne indskydes over en aksel til nøjagtig korrekt position på denne og derefter med stor kraft fastspændes til denne.it must be possible to slide easily over a shaft to the exact correct position on it and then fasten with great force to it.

5 I mange tilfælde kan det yderligere være hensigsmæssigt, såfremt udformningen også er som angivet i krav 6, hvilket er særlig fordelagtigt, såfremt de to spændeelementer tilsammen skal tjene som en akselkobling.In many cases, it may be further appropriate if the configuration is also as set forth in claim 6, which is particularly advantageous if the two clamping elements together serve as a shaft coupling.

10 Som foran nævnt vil et spændeelement ifølge opfindelsen have samme ændring af såvel inder- som yderdiameter. I mange tilfælde kan det imidlertid være fordelagtigt, såfremt spændeelementet kan bringes til at spænde såvel indad som udad, og dette kan ifølge opfindelsen opnås ved den i krav 7 angivne udformning.As mentioned above, a clamping element according to the invention will have the same change of both inner and outer diameter. In many cases, however, it can be advantageous if the clamping element can be caused to clamp both inwardly and outwardly, and this can be achieved according to the invention by the design according to claim 7.

1515

En sådan spændering kan f.eks. tjene til fastgørelse på en aksel af et transmissionselement med en konisk navboring. Ofte foretrækkes det imidlertid i nav at anvende cirkulærcylindriske navboringer, men også til sådant brug kan virkningen af koniske vederlagsflader hensigts-20 mæssigt udnyttes, nemlig såfremt udformningen yderligere er som angivet i krav 8. Forskydes de to sæt sektioner således, at det indvendige spændeelements sektioner søger at bevæge sig i retning ud af det udvendige spændeelement, vil dette søge at udvide sig, medens det indvendige vil søge at trække sig sammen. Yderligere vil de to spænde-25 elementer som følge af deres mod hinanden vendende koniske overflader tilpasse sig således efter hinanden, at såfremt det ene spændeelement er trykket så fast mod det organ, hvormed det skal bringes i indgreb, at det er vanskeligere at forskyde i forhold til dette end det andet spændeelement i forhold til det med dette samarbejdende organ, vil, det 30 være det sidstnævnte spændeelements ved den nævnte ende værende sektioner, som forskyder sig i forhold til det tilhørende organ, således at der kan sikres en ensartet fastpresning af det dobbelte spændeelement til begge tilhørende organer, samtidig med, at en fuldstændig koncentrisk fastgørelse mellem de to organer sikres.Such a tension can e.g. serve to attach to a shaft of a transmission element with a tapered hub bore. However, it is often preferred to use circular cylindrical hub bores in hubs, but also for such use, the effect of tapered baffle surfaces can be conveniently utilized, namely if the design is further as specified in claim 8. The two sets of sections are displaced such that the sections of the inner clamping member are displaced. seeking to move in the direction out of the exterior clamping member, this will seek to expand while the interior will seek to contract. Further, the two clamping members, due to their tapered surfaces facing each other, will adapt so that if one clamping member is pressed so tightly against the member by which it is to be engaged that it is more difficult to displace in relative to this than the other clamping member with respect to the cooperating member, the latter clamping member at said end section will be displaced relative to the associated member so as to ensure uniform compression of the clamping member. the double clamping member to both associated members, while ensuring complete concentric attachment between the two members.

De fornødne spændeorganer kan f.eks. anbringes på den måde, som fremgår 35 5The necessary clamping means can e.g. be placed in the manner indicated 35 5

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af den i krav 9 angivne udformning for spændeelementet, eller mere hensigtsmæssigt, men i fremstilling dyrere, af den i krav 10 angivne udformning.of the design of the clamping element according to claim 9, or more conveniently, but more expensive in manufacture, of the configuration of claim 10.

5 Opindelsen vil i det følgende blive nærmere forklaret under henvisning til tegningen, på hvilken fig. 1 viser et sidebillede af et på en aksel fastsiddende, som et nav udformet spændeelement ifølge opfindelsen, fig. 2 et tilhørende planbillede, 10 fig. 3 et sidebillede af et dobbelt spændeelement, der eksempelvis kan anvendes som kobling mellem to akselender, fig. 4 et sidebillede af et til fastgørelse på en radialvæg bestemt spændeelement ifølge opfindelsen, fig. 3 et til fig. 1 svarende billede af et af to spændeelementer 15 sammensat aggregat til fastspænding af eksempelvis en remskive på en aksel, fig. 6 på samme måde to samarbejdende spændeelementer til fastspænding af eksempelvis en remskive på en aksel, fig. 7 et planbillede af et spændeelement, der samtidigt kan spænde 20 såvel indad som udad, fig. 8 et sidebillede af endnu en udførelsesform for et spændeelement ifølge opfindelsen, fig. 9 et sidebillede, delvis i snit, gennem en udførelsesform for et dobbelt spændeelement ifølge opfindelsen bestående af et enkelt 25 spændeelement og et dette omsluttende andet spændeelement, fig. 10 et planbillede set i retning af pilen X i fig, 9, og fig. 11 en anden udførelsesform for et dobbelt spændeelement af den i fig. 9 viste art.The invention will be explained in more detail below with reference to the drawing, in which: FIG. 1 is a side view of a clamping member formed on a shaft as a hub according to the invention; FIG. 2 is a plan view, FIG. 3 is a side view of a double clamping element which can be used, for example, as a coupling between two shaft ends; FIG. 4 is a side view of a clamping element according to the invention for fixing to a radial wall; FIG. 3 is a view of FIG. 1 is a view similar to one of two clamping members 15 assembled for clamping, for example, a pulley on a shaft; 6 similarly two cooperative clamping elements for clamping, for example, a pulley on a shaft, fig. 7 is a plan view of a clamping member which can simultaneously clamp 20 both inwardly and outwardly; FIG. Fig. 8 is a side view of yet another embodiment of a clamping element according to the invention; 9 is a side view, partly in section, of an embodiment of a double clamping element according to the invention consisting of a single clamping element and a second clamping element enclosing it; FIG. 10 is a plan view of the arrow X in FIG. 9; and FIG. 11 shows another embodiment of a double clamping element of the embodiment shown in FIG. 9.

30 Det i fig. 1 og 2 viste spændeelement består af en cirkulær krans af ved elementets to ender skiftevis liggende henholdsvis primære sektioner 1 og sekundære sektioner 2 og er bestemt til at fastgøres på en glat aksel 3. Hver sektion 1 og 2 er udformet med i retning mod den modstående endeflade forløbende aksiale fremspring henholdsvis 4 og 5, 35 hvis endeflader henholdsvis 6 og 7 ligger i plan med det andet sektionssæts endeflader henholdsvis 8 og 9. Til sektionerne 2 med tilhø30 The FIG. 1 and 2, the clamping element consists of a circular wreath of alternately located at the two ends of the element, respectively, primary sections 1 and secondary sections 2 and is intended to be fixed to a smooth shaft 3. Each section 1 and 2 is formed with the opposite end faces extending axial projections 4 and 5, 35, respectively, whose end faces 6 and 7 respectively align with the end faces of the second section set 8 and 9, respectively.

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6 rende fremspring 5 er sluttet eger 10 af et transmissionselement 11, der er vist som en kileremskive. Spændeelementet udgør således et nav i dette transmissionselement.6 projection 5 is joined spokes 10 by a transmission element 11 shown as a V-belt pulley. The clamping member thus forms a hub in this transmission element.

5 Hver sektion 1 og 2 af den ene art er forbundet med de to hosliggende sektioner henholdsvis 2 og 1 af den anden art gennem mellemliggende ringpartier 12, der danner modsat vendende vinkler på mellem 15 og 60°, fortrinsvis mellem 20 og 45°, med radialplaner, og deres overgange til sektionerne 1 og 2 forløber fortrinsvis radialt, medens de selv som 10 følge heraf er vindel- eller skrue-formede om spændeelementets akse.Each section 1 and 2 of one species is connected to the two adjacent sections 2 and 1 of the other species, respectively, through intermediate ring portions 12, which form opposite angles of between 15 and 60 °, preferably between 20 and 45 °, with preferably, radial planes and their transitions to sections 1 and 2 extend radially, while as a result they themselves are spiral or helical about the axis of the clamping member.

Til spændeelementet hører et akslen 3 omgivende vederlag 13, der er vist udformet som en simpel ringplade. Vederlaget 13 er vist liggende ud for spændeelementets på tegningen opad vendende endeflader 6,9, og 15 den har på sin underside afstandsstykker 14, der alt efter pladens vinkelstilling i forhold til spændeelementet kan ligge an enten mod sektionerne 2's endeflader 9 eller mod fremspringene 4's opad vendende endeflader 6. Mellem afstandsstykkerne 14 er skiven udformet med glatte huller, hvorigennem bolte 15 kan skrues ind enten i gevindhuller 20 16 i de sekundære sketioner 2 eller i gevindhuller 17 i de primære sektioner l's fremspring 4.To the clamping element is a shaft 3 surrounding recess 13, which is shown as a simple ring plate. The cover 13 is shown adjacent to the end face faces 6,9 of the clamping element in the drawing, and 15 has on its underside spacers 14 which, depending on the angular position of the plate in relation to the clamping element, may be either against the end faces 9 of the sections 2 or against the projections 4 upwards. facing end faces 6. Between the spacers 14, the disc is formed with smooth holes through which bolts 15 can be screwed into either thread holes 20 16 in the secondary sketches 2 or into thread holes 17 in the projections 4 of the primary sections 1.

På tegningen ligger afstandsstykkerne 14 an mod fremspringene 4's endeflader 6, og boltene 15 er skruet ind i de sekundære sektioner 2's 25 gevindhuller 16. Når boltene 15 strammes, vil derfor de sekundære sektioner 2 blive søgt forskudt aksialt i retning væk fra de primære sektioner 1, hvorved de skrå ringpartier 12's hældning forøges, så at mel- mellemrummene mellem på hinanden følgende sektioner 1 og 2 formindskes og således spændeelementets inder- og yderdiameter reduceres, med det 30 resultat at spændeelementet og dermed transmissionselementet 11 urokkeligt fastspændes på akslen 3.In the drawing, the spacers 14 abut against the end faces 6 of the projections 4 and the bolts 15 are screwed into the threaded holes 16. of the secondary sections 2. As the bolts 15 are tightened, the secondary sections 2 will be sought to be displaced axially in the direction away from the primary sections 1. thereby increasing the inclination of the inclined ring portions 12 so as to reduce the gaps between successive sections 1 and 2, thus reducing the inner and outer diameters of the clamping element, with the result that the clamping element and thus the transmission element 11 are unshakably clamped on the shaft 3.

Drejes vederlaget 13 imidlertid så meget om akslen 3, at dens afstandsstykker kommer til at ligge an mod de sekundære sektioner 2's endefla-35 der 9, og følgelig boltene 15 bringes i indgreb med gevindhullerne 17 i sektionsfremspringene 4, vil de hertil hørende primære sektioner 1 7However, the remuneration 13 is rotated so much about the shaft 3 that its spacers abut against the end surfaces 9 of the secondary sections 2 and, consequently, the bolts 15 are engaged with the threaded holes 17 in the section projections 4, the associated primary sections 1 7

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blive søgt forskudt i retning mod de sekundære sektioner 2, så at ring-partierne 12's hældning formindskes, hvorved spændeelementets ind- og udvendige diameter forøges. Dette har betydning, såfremt spændeelementets inderdiameter i elementets neutralstilling kun har et ringe over-5 mål eller slet intet i forhold til akslen 3's diameter, idet den nævnte diameterforøgelse så medfører, at elementet alligevel let kan skydes ind over akslen til ønsket stilling. Når denne er nået, kan boltene 15 udtages, og vederlaget drejes, indtil dets afstandsstykker 14 ligger ud for fremspringene 4, så at boltene ved anskruning formindsker 10 spændeelementets diameter og sikrer en fastklemning på akslen 3.be sought to be displaced in the direction of the secondary sections 2 so as to reduce the inclination of the ring portions 12, thereby increasing the inner and outer diameter of the clamping member. This is important if the inner diameter of the clamping element in the neutral position of the element has only a slight overshoot or nothing at all with respect to the diameter of the shaft 3, since the said increase in diameter so that the element can still easily slide over the shaft to the desired position. Once this is reached, the bolts 15 can be removed and the recoil rotated until its spacers 14 are aligned with the projections 4, so that, by tightening, the bolts 10 reduce the diameter of the clamping element and ensure a clamping on the shaft 3.

Det skal bemærkes, at såfremt muligheden for en forøgelse af elementdi-ametrene ikke kræves, kan fremspringene 4 gives en større længde, så at et vederlag uden afstandsstykker altid vil ligge an mod fremspringenes 15 endeflader 6, men holdes i afstand fra de sekundære sektioner, ligesom kun disse behøver at udformes med gevindhullerne 16.It should be noted that, if the possibility of an increase in the element diameters is not required, the projections 4 can be given a greater length so that a remuneration without spacers will always abut the end faces 6 of the projections 15 but are kept away from the secondary sections. just as these need to be formed with the threaded holes 16.

I stedet for med vederlaget 13 fast forbundne afstandsstykker kan også anvendes løse sådanne, som anbringes efter behov.Instead of spacers 13 fixedly attached to the remuneration can also be used loose ones which are placed as required.

2020

Endelig skal bemærkes, at spændeelementet hensigtsmæssigt kan udformes således, at det er ens ved begge ender og ikke behøver at retningsorienteres ved anvendelsen.Finally, it should be noted that the clamping member can conveniently be designed so that it is similar at both ends and does not need to be directional in use.

25 Den foran nævnte mulighed for en forøgelse af elementdiametrene medfører, at elementet også kan bringes til at spænde udad mod indersiden af et rør eller en anden omgivende cylinderflade, f.eks. en navboring.The aforementioned possibility for an increase in the element diameters means that the element can also be caused to bend outwards towards the inside of a pipe or other surrounding cylinder surface, e.g. a hub bore.

Også mange andre modifikationer af spændeelementet er mulige. Det kan 30 således være polygonalt i stedet for cylindrisk, og dets inder eller yderside kan være konisk i stedet for cylindrisk. Yderligere kan di- mensionenre, herunder sektionerne l's og 2's bredde og aksiale længde samt de skrå ringpartier 12's tykkelse afpasses efter den tilsigtede anvendelse og inder- og ydersiderne af disse ringpartier 12 behøver 35 ikke at være sammenfaldende med de cylindriske eller koniske flader, der bestemmes af sektionerne 1 og 2.Many other modifications of the clamping element are also possible. Thus, it may be polygonal instead of cylindrical, and its inner or outer surface may be tapered instead of cylindrical. Further, the dimensions, including the widths and axial lengths of sections 1 and 2, as well as the thickness of the inclined ring portions 12, can be adapted to the intended application and the inner and outer sides of these ring portions 12 need not coincide with the cylindrical or tapered surfaces which are determined. of sections 1 and 2.

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88

Fig. 3 viser et dobbelt spændeelement bestående af to symmetrisk anbragte ringe baserede på det samme princip som elementet ifølge fig. 1 og 2, men fremstillet ved bukning af forholdsvis svært plademateriale.FIG. 3 shows a double clamping element consisting of two symmetrically arranged rings based on the same principle as the element according to fig. 1 and 2, but made by bending of relatively hard sheet material.

Hver pladering har skiftevis liggende, hvoedsageligt plane bølgetoppe 5 201 og bølgedale 202, der svarer til de primære sektioner 1 og 2 i fig.Each plate has alternating, substantially planar, wave peaks 5 201 and wave valleys 202 corresponding to the primary sections 1 and 2 of FIG.

1 og 2, og som er indbyrdes forbundet gennem skråtstillede ringpartier 212. Bølgetoppene 201 er ved elementernes udvendige omkredskant sammenhængende med flige 18, der strækker sig henholdsvis nedad og opad til elementets midter- eller symmetriplan og i dette har anlæg mod 10 hinanden, så at ringene danner hinandens vederlag. De to ringe er holdt sammen ved hjælp af bolte 213 svarende til boltene 15 i fig. 1 og 2. Et sådant dobbelt spændeelement kan f.eks. anvendes til sammen kobling af to akselender, og kan herunder udligne eventuelle mindre diameterforskelle mellem disse. Såfremt fligene 18 fastgøres til hinan-15 den ved berøringsfladerne, kan endog større diameterforskelle udlignes samtidig med, at de to akselender fastholdes konaksialt i forhold til hinanden.1 and 2, and which are interconnected through inclined annular portions 212. The wave peaks 201 are at the outer circumferential edge of the members contiguous with tabs 18 extending downwardly and upwards, respectively, to the center or symmetry plane of the element and having abutment with each other so that the rings form each other's consideration. The two rings are held together by bolts 213 corresponding to the bolts 15 of FIG. 1 and 2. Such a double clamping element can e.g. is used for the coupling of two shaft ends, and may include any smaller diameter differences between them. If the tabs 18 are attached to each other at the contact surfaces, even larger diameter differences can be compensated at the same time as the two shaft ends are held in contact with one another in relation to each other.

Fig. 4 viser et spændeelement, der svarer til et af de to i fig. 3 vi-20 ste enkeltelementer, idet dog fligene 18 er udeladte. Til gengæld strækker der sig fra hver bølgetop 201 aksialt et fremspring 204, hvis ende er beliggende uden for det fælles plan for bølgedalene 202's endeflader. Disse fremspring 204 ligger an mod en som vederlag tjendende radial endevæg af et organ 19, f.eks. et nav, der skal fastgøres til 25 akslen 3, og hvormed spændeelementet er forbundet ved hjælp af boltene 215, som er ført gennem glatte boltehuller i bølgedalene 202 og skruet ind i gevindhuller i organet 19's nævnte væg.FIG. 4 shows a clamping member corresponding to one of the two in FIG. Three separate elements, with the exception of the tabs 18, are omitted. In contrast, from each wave peak 201 axially extends a projection 204, the end of which lies outside the common plane of the end faces of the wave valleys 202. These projections 204 abut against a radial end wall serving as a consideration 19 by means 19, e.g. a hub to be secured to the shaft 3 and to which the clamping element is connected by the bolts 215 which are passed through smooth bolt holes in the wave valleys 202 and screwed into thread holes in the wall of the member 19.

Fig. 5 viser, hvorledes et dobbelt spændeelement bestående i alt 30 væsentligt af to spændeelementer af den i fig. 1 og 2 viste art, kan anvendes til såvel fastspænding af et organ 11, f.eks. et transmissionselement, til spændeelementet som fastspænding af dette til en aksel 3. Det på tegningen nederst viste spændeelement, der er indsat i f.eks. en navboring, er udformet på samme måde som spændeelementet i-35 følge fig. 1 og 2, idet dog de primære sektioner 1 med tilhørende fremspring 4 er udformede med gennemgående glatte huller for boltene 15, 9FIG. 5 shows how a double clamping element comprising a total of 30 substantially of two clamping elements of the embodiment shown in FIG. 1 and 2 can be used for both clamping of a member 11, e.g. a transmission element, for the clamping element as clamping this to a shaft 3. The clamping element shown in the drawing below, inserted into e.g. a hub bore is configured in the same manner as the clamping element of FIG. 1 and 2, however, the primary sections 1 with associated projections 4 are formed with through smooth holes for the bolts 15, 9

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hvis gevinddele er skruet ind i gevindskårne huller i det øverste spæn-deelements primære sektioner, hvis endevægge 8 er noget tilbagetrukket i forhold til endevæggene 7 af de sekundære sektioners fremspring 5, hvilke endevægge ligger an mod det nederste spændeelements sekundære 5 sektioner 2's endevægge 9. Ved antrækning af boltene 15 vil det øverste spændeelement indsnævres og fastspændes på akslen 3, medens det nederste spændeelement vil udvide sig og derved fastspændes inde i den omsluttende navboring i organet 11. Intet forhindrer i øvrigt, at de to spændeelementer kan fremstilles i ét.the threaded portions of which are screwed into threaded holes in the primary sections of the upper clamping member, the end walls 8 of which are somewhat retracted with respect to the end walls 7 of the projections 5 of the secondary sections, which end walls abut the end walls 9 of the lower clamping member 5. By tightening the bolts 15, the upper clamping member will narrow and clamp onto the shaft 3, while the lower clamping member will expand, thereby clamping within the enclosing hub bore of the member 11. Nothing further prevents the two clamping members from being manufactured in one.

1010

Fig. 6 viser, hvorledes to spændeelementer af den i fig. 4 viste art kan anvendes til fastspænding af f.eks. et transmissionselement 11 på en aksel 3 ved anbringelse inden i en navboring. Til dette formål er det vederlag, der i fig. 4 udgøres af en navendevæg, erstattet med ko- 15 niske indgrebsflader 20 for spændeelementet , idet navboringens indven dige omkredsflade udgøres af to ens, men modsat vendende keglestubfla-der 20 med en lille topvinkel, og de to spændeelementers udvendige omkredsflader er koniske på tilsvarende måde. Herved kan det sikres, at de to spændeelementer ved antrækning af de bølgedalene 202 forbindende 20 bolte 215 både indsnævres om akslen 3 og kiles fast i navboringen, så at delene forbindes udrejeligt i forhold til hinanden.FIG. 6 shows how two clamping elements of the embodiment shown in FIG. 4 can be used for clamping e.g. a transmission element 11 on a shaft 3 by placement within a hub bore. For this purpose, the remuneration shown in FIG. 4 is made up of a hub wall, replaced by conical engaging surfaces 20 of the clamping element, the inner circumferential surface of the hub bore being two similar but opposite facing cone stub surfaces 20 with a small top angle and the outer circumferential surfaces of the two clamping elements correspondingly . In this way, it can be ensured that the two clamping elements, by tightening the 20 valves 202 connecting 20 bolts 215, are both narrowed about the shaft 3 and wedged in the hub bore so that the parts are extensible to each other.

Fig. 7 viser skematisk et spændeelement af den i fig. 4 viste art, men således udformet, at det på samme tid kan spænde indad, f.eks. om en 25 aksel og udad, f.eks. mod en navborings indervæg. Ved denne udførel sesform er bølgetoppene 201 og tilstødende skrå ringpartier 212 stanset og presset ud af en skive 11, så at der i denne ud for de nævnte spændeelementdele er dannet en åbning 22, medens de mellem åbningerne værende skivedele udgør spændeelementets bølgedale eller se-30 kundære sektioner 202. Bag skiven 21, støttende mod bølgedalene 202, men kun delvis dækkende åbningerne 21, er anbragt et vederlag 13, der kan fastholdes til skiven 21 ved hjælp af i bølgedalene indskruede bolte 23. Gennem gevindhuller 217 i bølgetoppene 201 kan ikke viste bolte skrues til anlæg mod vederlaget 13, så at bølgetoppene 201 kan 35 tvinges i retning bort fra vederlaget. Skiven 21, der er fremstillet af et elastisk eftergivende materiale, og som i det væsentlige er cir- 10 DK 155167 B | i kulær-cylindrisk, men ud for bølgedalene 202 har udvendige affladninger 33, vil ved den nævnte presning af bølgetoppene 201 bort fra vederlaget 13 som følge af åbningerne 22 udvide sig og kan således bringes til fast anlæg mod en omsluttende væg, hvorimod skiven 21's inderdel ved 5 den nævnte udpresning vil blive givet en reduceret inderdiameter.FIG. 7 shows schematically a clamping element of the embodiment shown in FIG. 4, but designed so that it can at the same time span inwardly, e.g. about a 25 shaft and outwards, e.g. against the inner wall of a hub bore. In this embodiment, the wave peaks 201 and adjacent oblique ring portions 212 are punched and pressed out of a washer 11, so that an opening 22 is formed next to said clamping member portions, while the disc portions between the apertures constitute the wave valves of the clamping member or lateral 30. posterior sections 202. Behind the disc 21, supported by the wave valleys 202, but only partially covering the openings 21, is provided a consideration 13 which can be secured to the disk 21 by means of bolts screwed into the wave valves 23. Through thread holes 217 in the wave peaks 201 can not be shown. bolts are bolted to abutment against the consideration 13 so that the wave peaks 201 can be forced in a direction away from the consideration. The disc 21, which is made of a resilient resilient material and which is substantially circular 10 155157 B | in the cylindrical cylindrical form, but outside the wave valleys 202 have external discharges 33, at the said pressing of the wave peaks 201, away from the compensation 13 as a result of the openings 22, it can expand and thus can be brought to a fixed abutment against an enclosing wall, whereas the inner part of the disc 21 at 5 the said extortion will be given a reduced inner diameter.

Fig. 8 viser et spændeelement af samme art som det i fig. 1 og 2 viste, men med en konisk yderside, som passer ind i en indvendigt konisk og udvendigt cylindrisk mellembøsning 24, der på kendt, ikke nærmere vist 10 måde er udformet med fra begge ender udgående og ind mellem hverandre sig strækkende slidser med mindre længde end bøsningens bredde.FIG. 8 shows a clamping element of the same kind as that of FIG. 1 and 2, but with a conical exterior, which fits into an inner conical and outer cylindrical intermediate sleeve 24, which in a known, not further shown manner, is formed with slits of smaller length extending from each end and between each other. than the sleeve width.

Bøsningen, der således er eftergivelig, er indsat i en navboring i et transmissionselement 11. Selve spændeelementet består af skiftevis liggende sektioner 1 og 2 med mellemliggende skrå ringpartier 12. Et 15 skiveformet vederlag 13 ligger an mod bøsningens tykke ende og bærer bolte 15, der er skruet ind i de sekundære sektioner 2, så at disse ved antrækning af boltene trækkes i retning mod vederlaget 13, hvilket imidlertid modvirkes af mod hinanden anliggende koniske flader i bøsningen og på spændeelementet. Spændeelementet vil således ved boltenes 20 antrækning, som foran forklaret, bringes til samtidigt at trykke ind mod akslen 3 og presse udad mod bøsningen 24, hvorved denne også udvider sig og klemmes fast i navet 11's navboring.The sleeve thus resiliently is inserted into a hub bore of a transmission element 11. The clamping element itself consists of alternating sections 1 and 2 with intermediate inclined ring portions 12. A 15 disc-shaped support 13 abuts the thick end of the sleeve and carries bolts 15 which are screwed into the secondary sections 2 so that, when the bolts are tightened, they are pulled in the direction towards the support 13, which is, however, counteracted by abutting tapered surfaces in the bushing and on the clamping element. Thus, at the tightening of the bolts 20, as explained above, the clamping element will be caused to simultaneously push against the shaft 3 and push outwards against the bushing 24, thereby also expanding and clamping in the hub bore of the hub 11.

Fig. 9 og 10 viser en udførelsesform for et dobbelt spændeelement iføl-25 ge opfindelsen udformet, så at det danner en spændebøsning til indskydning mellem en aksel 3 og en ikke vist navboringsinderside. Denne spændebøsning består af to spændeelementer 25 og 26 af den i fig. 1 viste art, af hvilke det inderste 25 har en konisk yderside, men cylindrisk inderside, medens det udvendige har en cylindrisk yderside 30 og en konisk inderside af samme størrelse som og med samme konicitet som inderelementet 25's ydersider. For de to elementer 25 og 26's enkeltdele er anvendt samme betegnelser som i fig. 1, men idet der til betegnelserne for elementet 25's vedkommende er tilføjet angivelsen " 1 ", og for elementet 26's vedkommende betegnelsen De to elementer 35 er anbragt således, at til hinanden svarende dele i de to elementer ligger lige ud for hverandre, dvs. sektionerne 1' i det indvendige ele-FIG. Figures 9 and 10 show an embodiment of a double clamping element according to the invention designed to form a clamping bush for insertion between a shaft 3 and a hub bore not shown. This clamping sleeve consists of two clamping members 25 and 26 of the one shown in FIG. 1, of which the inner 25 has a conical exterior but cylindrical inside, while the exterior has a cylindrical exterior 30 and a conical inside of the same size as and of the same conicity as the exterior of the inner element 25. For the individual parts of the two elements 25 and 26, the same designations as in FIG. 1, but with the designation "1" for the element 25, and for the element 26 the designation The two elements 35 are arranged so that corresponding parts of the two elements are equal to each other, ie. the sections 1 'of the inner ele-

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11 ment 25 ligger ud for sektionerne 1M i det udvendige element 26, medens det samme gælder for sektionerne 2' og 2''. Det indvendige spæn-deelement 25's fra de sekundære sektioner 2' udgående fremspring 5' bærer udad ragende øjer 25, der ikke strækker sig uden for spændeelemen-5 tet 26's yderside, og som ligger ud for det udvendige spændeorgan 26's sekundære sektioner 21' 's inderender, idet disse sektioner ikke har fremspring svarende til fremspringene 5. Øjerne 27 har aksialt forløbende glatte boltehuller til optagelse af bolte 28, som er skruet ind i gevindhuller 16'' i det udvendige spændeelements sekundære sektioner 10 2".11 ment 25 is adjacent to sections 1M of the outer member 26, while the same applies to sections 2 'and 2' '. The internal protrusion 25 of the secondary projections 5 'extending from the secondary sections 2' carries outwardly projecting eyes 25 which do not extend outside the outer side of the clamping element 26 and which lie outside the secondary sections 21 'of the external tensioning member 26'. The ends 27 have axially extending smooth bolt holes for accommodating bolts 28 which are screwed into threaded holes 16 '' in the secondary sections 10 2 of the outer tension member.

Trækkes boltene 28 an, vil det udvendige spændeelement 26's sekundære sektioner 2'' blive trukket i retning mod de tilhørende primære sektioner l1', således at det udvendige spændeelement 26 udvider sig, men 15 samtidig vil det indvendige spændeorgan 25's primære sektioner 1' blive trukket i retning af de tilsvarende sekundære sektioner 2', så at det indvendige spændeelement sammentrækkes og spænder om akslen 3. Udvidelsen af det udvendige spændeelement 26 medfører, at dette fastspændes i den, ikke viste, navboring, hvori det dobbelte spændeelement er 20 indsat.If the bolts 28 are tightened, the secondary sections 2 '' of the external clamping member 26 '' will be pulled in the direction of the associated primary sections 11 ', so that the external clamping member 26 expands, but at the same time the primary sections 1' of the internal clamping member 25 'will be pulled. in the direction of the corresponding secondary sections 2 ', so that the internal clamping member is contracted and tightening about the shaft 3. The expansion of the outer clamping member 26 causes this to be clamped in the hub bore (not shown) in which the double clamping member 20 is inserted.

Et tværsnit gennem et tilsvarende, en spændebøsning dannende dobbelt spændeelement er vist i fig. 11. Her er dog hver spændeelement 25 og 26 kun udformet med tre sektioner 1 og 2 ved hver ende, medens der i 25 udførelsesformen ifølge fig. 9 og 10 er seks sektioner ved hver ende. I denne udførelsesform er ved overgangen mellem de to spændeelementers mod hinanden anliggende sektioner 2' og 2'' fra den tilstødende endeflade udbaret et hul 29,30, der strækker sig ind i begge sektionerne 2' og 2'*, men idet huldelen 29 i sektionen 2" er glat og har en afgræn-30 set længde, medens huldelen 30 i sektionen 2' er gevindskåret og har en længde, som er større end huldelen 30's. Indskrues bolte i disse huller, vil sektionerne 2'' ved skruens anlæg mod huldelen 29's bund blive skudt til venstre i figuren, hvilket bevirker en udvidelse af det udvendige spændeelement 26, samtidig med, at sektionen 2' vil blive 35 trukket mod højre, hvilket bevirker en sammentrækning af det indvendige spændeelement 25.A cross section through a corresponding double clamping member forming a clamping sleeve is shown in FIG. 11. Here, however, each clamping member 25 and 26 is formed only with three sections 1 and 2 at each end, whereas in the embodiment of FIG. 9 and 10 are six sections at each end. In this embodiment, at the transition between the adjacent sections 2 'and 2' 'of the two clamping members, a hole 29,30 extending into both sections 2' and 2 ' the section 2 "is smooth and has a defined length, while the hollow part 30 of the section 2 'is threaded and has a length greater than the hollow part 30's. Bolts are bolted into these holes, the sections 2' 'at the screw's abutment will against the bottom of the hollow member 29 is pushed to the left in the figure, causing an expansion of the outer clamping member 26, while the section 2 'will be pulled to the right causing a contraction of the internal clamping member 25.

Claims

1. Clamping means for e.g. fixed enclosure of a shaft or fixture for fixed abutment against an inner circumferential surface and having at least one clamping element having a circumferential length which is variable by mutually axial displacement in opposite directions from the unloaded position of the element evenly distributed on the two opposite radial sides element parts, characterized in that the clamping element or each has two sets of two opposite sides of the element facing in the axial direction alternating sections (1 and 2), primary and secondary sections, each of which are connected to the two adjacent sections through relative to the axial direction, inclined ring portions (12) forming an angle of between 15 ° and 60 °, preferably between 20 ° and 45 °, with radial planes and whose inclination is at least somewhat variable at forced axial displacement of the two section sets (1 and 2) relative to each other. 30

Clamping member according to Claim 1, characterized in that one set of sections (2) has a fixed end face (9) for fixed abutment (13) in a radial plane, while the other set of sections (1) has their end faces (6) facing in the same direction are spaced apart from said radial plane and are adapted to receive shear means (15) with which they can be displaced forcibly towards the consideration (13). DK 155167 B

Clamping device according to claim 1, characterized in that the sections (1) in one set of sections have in the direction of the common radial plane of the end faces (4) of the second section set (2) the projections (4), whose end faces (6) are also located. in this radial plane, and that a clamping ring (13) belongs to the clamping element, one side of which faces the said end faces (6 or 9) and which carries spacers (14) forming abutment surfaces for said end faces of the one element set.

Clamping member according to claim 3, characterized in that the spacers (14) are fixedly connected to or formed integrally with the clamping ring (13) and that it is pivotally connected to the clamping element in such a way that the spacers ( 14) in one position of the recoil ring (13) lies opposite the end faces (6 or 9) of one section set and in another adjacent the end faces (9 or 6) of the other section set. 20

Clamping member according to claim 1, characterized in that it has two cooperating clamping elements, the sections of which of which one section set (2) of the one element forms a consideration for the corresponding section set of the other element, while the other section set (1) of the two elements. are interconnected by means of clamping means (15), e.g. bolts with which they can be pressed in a direction towards each other.

Clamping member according to Claim 1, characterized in that the external or internal surface of the clamping member is conical and intended to serve as abutment surface for a conical surface serving as a consideration, respectively, in a surrounding member, e.g. a pulley or cog hub, or on an enclosed member, e.g. a shaft.

Clamping member according to claim 6, characterized in that it consists of two clamping elements (25 and 26), one of which has an exterior tapered surface, while the other has an inner one and with it is projected into it. the former element having its sections (1 "and 2") adjacent to its 5 corresponding sections (1 'and 2'), the clamping elements (25 and 26) having parts (27 or 29, 30) with which the external clamping element (26 ) at its end with at least inner diameter sections (2 ") are axially displaceable relative to and in the opposite direction of the inner member (25) at sections (21) at the same end.

Clamping member according to claim 7, characterized in that the inner clamping element (25) at the end with the largest diameter sections or section parts (5 ') has side projections (27) next to the outer clamping element (26) at the opposite end. are sections (2 "), each side projection of which has a smooth threaded hole for a bolt (28), the threaded of which can be screwed into a threaded hole (16") in the opposite section (2 ") of the outer tension member or an axial extension thereof.

Clamping member according to claim 7, characterized in that at the end where the inner clamping element (25) is of least diameter, known per se in part partly in one 25 and partly in the other of each pair of sections here (2 'and 2 ") an axially extending hole (29, 30) is formed if the hollow portion (29) of the outer tension member (26) section (2") is smooth and of limited length while in the interior tension member (25) being hollow member (30) is threaded and has a greater length than the hollow member (29) in the outer v U tension member (26). 35