WO2008066469A1 - Method and device for torque transmission - Google Patents
Method and device for torque transmission Download PDFInfo
- Publication number
- WO2008066469A1 WO2008066469A1 PCT/SE2007/050763 SE2007050763W WO2008066469A1 WO 2008066469 A1 WO2008066469 A1 WO 2008066469A1 SE 2007050763 W SE2007050763 W SE 2007050763W WO 2008066469 A1 WO2008066469 A1 WO 2008066469A1
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- WIPO (PCT)
- Prior art keywords
- cross
- force
- sectional dimension
- gap
- larger
- Prior art date
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Classifications
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- 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
- F16D41/00—Freewheels or freewheel clutches
- F16D41/06—Freewheels or freewheel clutches with intermediate wedging coupling members between an inner and an outer surface
- F16D41/069—Freewheels or freewheel clutches with intermediate wedging coupling members between an inner and an outer surface the intermediate members wedging by pivoting or rocking, e.g. sprags
- F16D41/07—Freewheels or freewheel clutches with intermediate wedging coupling members between an inner and an outer surface the intermediate members wedging by pivoting or rocking, e.g. sprags between two cylindrical surfaces
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- 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
- F16D1/08—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 with clamping hub; with hub and longitudinal key
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- 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
- F16D15/00—Clutches with wedging balls or rollers or with other wedgeable separate clutching members
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- 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
- F16D2001/062—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 characterised by adaptors where hub bores being larger than the shaft
Definitions
- the present invention relates to a method for moment transmission, preferably torque transmission, between a first object and a second object that are separated by a gap, the method comprising the arranging in said gap of a force-transmitting device that comprises at least one flexible element and a plurality of force-transmitting elements that are preferably not part of the flexible element but are arranged at said flexible element, and the arranging of said force-transmitting elements to have a maximum cross-sectional dimension that is larger than the gap and another cross-sectional dimension that is smaller than the gap, in order by friction by wedge action to transmit a moment between said first object and said second object.
- the invention also relates to a coupling device for working the method.
- the present invention (product) relates to equipments, preferably in connection with machines in which a shaft is coupled together with a hub.
- the hub may, in its turn be formed as and/or associated with a shaft coupling half, a cog wheel, a belt pulley, a pump or turbine wheel or any other element that is to be coupled to a shaft or a similar element.
- Known constructional elements for the coupling can largely be classified as shape determined, such as a key joint, or friction determined, such as a press joint or a friction joint with a conical sleeve. More specifically, the invention relates to the field of friction joints having essentially cylindrical surfaces for the shaft and the hub.
- tolerance rings consist of a strip that is undulated in its tangential direction.
- the radial extension of the waves of the undulation is larger than the radial gap between the cylindrical surfaces of a shaft and a hub that are to be coupled together.
- a moment is transmitted by friction from the normal force that arises from the strip when it has been mounted in the gap. The transmitted moment is directly dependent on the axial force that is required when the details are mounted.
- the device comprises a (steel) strip that is pressed to different thicknesses (in a machine), is punched to a certain shape with recesses and is then bent to give a tangentiaUy corrugated shape.
- the strip is defined as "endless” and thereby it can be reeled up. Before mounting a suitable length is cut and bent to the appropriate circular shape for a shaft and is hardened. Probably, many problems will arise in connection with this device, among others relating to tolerances of the distance between contact points for force transmitting parts (thicker parts), which probably explains its obviously limited commercial use.
- a device that comprises a strip as the main element.
- the strip has parts that are U-shaped in the tangential direction, which parts, similar to tolerance rings, are larger than the radial gap. These parts can transmit a moment (hereinafter mostly referred to as torque) in two directions by the obliqueness adjusting itself to the direction of the torque.
- torque a moment
- the obliqueness is achieved by elastic deformation of the U-shaped part, i.e. the part on which the force acts.
- the contact surfaces against the shaft and the hub are shown to have very small radii of curvature, which is probably necessary in order for the strip to be able to transmit a torque without slippage.
- the device gives a lower mounting force in the axial direction than a traditional tolerance ring does, but the very thin part in the U-parts must lead to a considerable weakness, resulting in that they are buckled or crushed. In many applications this is a major disadvantage.
- a so called freewheel US 4,809,831
- a holder for elements with a section shape like a "peanut shell" The elements are of complex shape with recesses in the side surfaces for secure retaining in central recesses in a "continuous" strip.
- the elements are arranged to move freely in these recesses and are retained by the creation of an obstruction in the strip in order for the elements not to be able to fall out.
- the device is relatively complex and thereby expensive to manufacture. Free-wheel elements are moreover normally made in hardened steel to operate against hardened surfaces, which makes them even more expensive.
- the improvement achieved by the invention relates primarily to an improved ability to transmit a torque; the enabling of larger allowed dimensional variations due to tolerances in the radial gap; the enabling of a lower contact pressure according to Herz, which results in less permanent deformations and less risk that the force-transmitting elements (hereinafter called pin/pins) are crushed or buckled due to the arising forces.
- pins are positioned in a radial gap "g", preferably between cylindrical surfaces for a shaft and a hub. These pins have at least one radial cross-sectional dimension in the assembled state that is smaller than the gap and another one that is larger than the gap.
- a wedge action may arise.
- Figs. IA, B show a part of a coupling device, in a side view
- Fig. 2 shows a view in perspective as seen obliquely from above, of a force- transmitting element/pin
- Fig. 3 shows a view in perspective as seen obliquely from above, of a locking device adapted to be used in connection with the invention when this is used in circular gaps.
- Fig. 4 schematically shows a side view of coupling device in a combined circular shape
- Fig. 5 shows a cross-section in a side view, of a part of a coupling device mounted between a shaft and a hub
- Figs. 6A, B schematically show side views that illustrate some principles of the function of a pin
- Fig. 7 schematically shows a principle side view of an alternative embodiment of a pin
- Fig. 8 schematically elucidates the functioning principles of a pin according to Fig.
- Fig. 9 schematically shows a side view of yet an alternative of a pin
- Figs. 1 OA, B show an alternative configuration of a coupling device, in a side view
- Fig. 11 schematically shows an alternative coupling device in a cross-sectional side view
- Fig. 12 shows, in cross-section, a part of a pin with an assembled strip
- Fig. 13 shows an alternative with a woven mat
- Fig. 14 shows a cross-section along line XTV-XTV in Fig. 13 ,
- Fig. 15 shows a cross-section along line XTV-XTV in Fig. 13,
- Fig. 16 shows a view of an alternative with pins and flexible element integrated
- Fig. 17 shows a cross-section of pins that are held together by the geometrical shape of the pins
- Figs. 18A, B show end views of pins intended for a radial gap with large variations
- Figs. 19A, B show side views of pins according to Fig. 18A mounted between the shaft and the hub
- Fig. 20 shows in perspective from above a view of an alternative flexible element for an embodiment according to Fig. 19.
- Figs. IA and IB show a first embodiment as side views of a part of a coupling device 1 according to the invention.
- Fig. IA shows a contemplated position that arises when the pins 2 in the device 1 are pressed between an upper and a lower contemplated plane, such that these are parallel and uniform, with the purpose of illustrating the shape of two strips 3 A, 3B that hold together the pins 2.
- Fig. IB shows the device 1 in a non-affected state, in which the strips 3 A, 3B are in one and the same plane.
- the figures show that the coupling device 1 consists of a number of pins 2 that in cross-section have a certain representative width b, as measured transversely to (i.e.
- a vertical dimension a that will be explained in greater detail below, hi this embodiment, the dimension a is shown to be larger than the width b and smaller than the maximal cross- sectional dimension c of the pin.
- the pins 2 are united/attached by a flexible element, here in the form of two strips 3 A, 3B, at either end 2OA, 2OB (Fig. 2) of the respective pin 2.
- the strip 3A is flexible and has certain elasticity and its objective is to be able to affect the pins 2 elastically to be positioned as desired in the radial extension, Le. a direction that is essentially perpendicular in relation to the extension L of the strip, and also to fix each pin 2 in a certain position in relation to other pins 2 at the strip 3A.
- the embodiment in Figs. IA, IB shows a device with "neutrally positioned" pins 2, in which each pin 2 is intended to take part in torque transmission in two opposite directions.
- the pins 2 are suitably riveted together by pressing of the ends 2OA, 2OB of the pins to the strip 3 A, 3B, to form them into a kind of mat.
- the flexible element is preferably formed as a strip, which means that the mat becomes flexible across the longitudinal direction of the pins and stiff along the same.
- the joining together can take place by other methods such as welding, gluing etc.
- each pin 2 comprises a central solid portion 21, that has four sides 25, 26, 27, 28, of which two are essentially opposing contact surfaces 25 and 28, that comprise bent opposing contact zones 25', 28" and 25", 28' respectively (Fig. 8).
- the contact zones 25', 25", 28', 28" are shaped to have a curvature radius r (Fig. 1) the size of which is essential to the invention.
- the contact zones hold the surfaces that are intended to be active by friction/clamping action in order to transmit a torque, e.g. from a shaft 4 to a hub 5 (Fig. 5).
- the pins 2, that are shown for example in Figs. 2 and 8, are double-acting and have two pairs of opposing contact zones 25", 28' and 25', 28", which interact in pairs. One pair is intended to transmit a torque in one direction and the other pair in the opposite direction, hi case of the transmission of a torque there is line contact between the pin 2 and the shaft 4 and the hub 5, respectively, at the two opposing contact points ki, Hi 1 (Fig.
- a maximum height dimension a max (Fig. 8) can be less than the maximum cross-sectional dimension c of a pin (Fig. IA), and that the height dimensions for a contact zone lie in a range a to a ⁇ .
- Each pin 2 has a longitudinal extension 1 (Fig. 2) that is considerably larger than the vertical dimension of the pin, preferably 1 > 10 a, whereby each pin 2 gets a long and narrow configuration.
- a major advantage of this long and narrow configuration is that a considerable saving in material is achieved without lowering the torque transmitting capacity of the device.
- On either side of the central portion 21 are the ends 2OA, 20B of the pin, in the following denoted positioning portions 20 A, 2OB, that have a smaller longitudinal extension I 1 than the longitudinal extension 1" of the central portion 21.
- a long and narrow recess is arranged in the form of a groove (a slot) 24 in the respective positioning portion 20A and intended to accommodate and fix the pin 2 at a first 3 A and a second 3B strip, respectively.
- the grooves 24 are vertically displaced such that the grooves 24 at one end are positioned above the
- the opening s in the groove 24 is adapted to the thickness s' of the strip 3 A, 3B, Le. it is large enough to enable the mounting of the pin 2 on the strip and subsequent fixing at the strip.
- steel strips 3 A, 3B are used that have a thickness of about 0.05-0.5 mm, made of a spring steel of suitable elasticity.
- the opening s of the groove 24 is given a suitable tolerance to be about 0.01 - 0.1 mm larger than the than the thickness of the strip.
- FIG. 3 shows, in a perspective view, a locking device intended to be used to bend a coupling device 1 and intraconnect it to form an approximately circular coupling device 1 (Fig. 4).
- the locking device 6 consists of a central straight or bent plate-shaped part 60 from which a first 61 and a second 62 locking leg extend perpendicularly, which locking legs 61, 62 are provided with a groove 63 adapted to receive one of the two strips 3A, 3B.
- a few spacers 9 advantageously can be used, which are positioned at essentially regular distances among the pins 2.
- the spacers 9 are made e.g. with a completely circular cylindrical outer periphery and are suitably tube-shaped with an open or closed section in order to be radially flexible.
- the function of the spacers 9 is to assist in the centring of a hub 5 in relation to a shaft 4, between which a coupling device 1 according to the invention is arranged.
- the spacers 9 maintain a desired uniform gap g between the hub 5 and the shaft 4.
- the spacing between the spacers 9 in a mat is chosen such that there are at least three spacers for a given shaft diameter d.
- the cylindrical shape need not be used but can be replaced with any shape that, with adequate accuracy, is able to fill the gap g and centre the hub at the shaft.
- the centring is made e.g. by pins 2 that are longitudinally bent 3G (Fig. 11).
- Fig. 5 shows in cross-section a coupling device 1 according to Fig. 4, positioned to give permanent contact between a shaft 4 and a hub 5 in the gap g them between.
- the elasticity in the strips 3 A, 3B will affect the pins 2 to alternately abut with one end (an outer contact point k2) against the hub 5 and with the other end (inner contact point ki) against the shaft 4.
- Fig. 6B-8 illustrate that the torque transmission, including some axial and radial forces, take place by the specially shaped pins 2 according to the invention.
- the shape of the pins 2 is such that a wedge action by friction will transmit the torque, from a first part 4 to a second part 5.
- the curvature radii r of a pin 2 at the contact zones 25', 25" and 28', 28", respectively, in Fig. 8 denoted rs and rh, respectively, where s denotes "shaft” and h denotes "hub”, are suitably larger than half the smallest cross-sectional dimension of the pin a, i.e. ⁇ s>Vra. and rh ⁇ /ra, respectively.
- a representative value of the smallest cross-sectional dimension b of the pin (this is suitably also true for a dimension b' (Fig. 7) measured in a direction that is approximately tangential when the pin is mounted between the shaft and the hub) is larger than a fourth of the dimension a or b > V*-a and preferably b>l/3-a and more preferred b>V2-a.
- This size of b is also necessary in order to prevent that the pin 2 is crushed when loaded, thereby resulting in serious errors and failure to operate.
- the dimension b also determines the possible variations of the gap and its tolerance X.
- the variation X is considerable in practice as it does not only comprise production tolerances for the shaft 4, hub 5 and pins 2, but also elastic and plastic deformations in these parts resulting from load.
- the wall thickness of the hub and the shaft, particularly a hollow shaft can be made small which results in considerable cost savings.
- the smaller wall thickness will increase the elastic deformations and thereby the variation of X.
- Fig. 8 shows an embodiment in which a ⁇ ⁇ c, i.e. in which the contact zones 25', 25", 28', 28" reach almost the entire way out to the outermost point of the corner zone and in which the entire contact sides 25, 28 are used as contact zones 25', 25" and 28', 28", respectively, which means that there need not be a gap between the contact zones, i.e. 25' and 25" meet each other at the middle of the contact side 25.
- the dimension a can generally be said to be equal with the gap g when the invention is used between a hub 5 and a shaft 4 having a given diameter d.
- the dimension a can be measured directly at the pin 2 (Fig. 6B) which is not the case in connection with opposed pins 2 of specific shape (Fig. 7).
- the points ki', Hi 1 '; k]", In 1 " that in Fig. 6 are marked with rings are contact points at the smallest and the largest radial play X, respectively, hi connection with a torque load with the smallest play, the resulting forces of friction and of the normal forces act along the dotted line F 1 between ki' and Hi 1 '.
- a corresponding line F 2 results between the outer points k t ", Ui 1 ".
- the area between the central points at the top and at the bottom is normally not used.
- the smallest radial play X is suitably determined in consideration of simple assembly of the device 1 and its pins between the shaft 4 and the hub 5 and is about 0.01 % of the shaft diameter or about 0.2 % of "a".
- the largest play X is determined by the dimension b and the operating area of the flexible element, and for practical reasons it is of the magnitude of 5 % of "a".
- the radial play X can however be of the magnitude of 25 % of 1 (Figs. 18, 19).
- Pins 2 which are positioned to be opposing (Figs. 10A, 10B), may have a strongly reduced sectional shape (Fig. 7).
- the cross-sectional shape in Fig. 7 is taken as a part of the shape in Fig. 6B, namely containing only one pair of opposing contact zones 25", 28", as such a reduced pin 2 is intended to act only in a single direction whereas another similar one, but opposing, pin acts in the opposite direction.
- Fig. 7 also shows the dotted line F 1 for the line of action of the forces at the smallest radial play.
- the measure of the dimension a can be identified, but the measuring requires knowledge of an angle ⁇ .
- This practical method gives an accuracy for the measuring of a, which is considerably better than 1 A percent.
- the dimension a is the smallest dimension that has an angle ⁇ that is larger than zero and at the same time smaller than a certain maximum value.
- a wedge action with longitudinal or tangential force transmission is namely based on that the contact points k ⁇ and Jn 1 are not positioned directly opposite each other, but that a connection line F them between forms an angle ⁇ against a normal to parallel tangents in these points.
- the largest dimension a max is the largest dimension that has an angle ⁇ larger than zero and smaller than a certain maximal value.
- the maximum value of the friction angle is hence limited to about 12° for "natural" untreated contact zones and 24° for those prepared to have a large friction coefficient, see also below.
- the contact zones are hence the areas where the angle ⁇ is larger than zero and less than a certain value, irrespective of if the entire areas are used in a certain application or not.
- the curvature radii rs and rh in the contact zones in the contact sides 28 and 25, respectively, determine the transmittable torque by the size of the contact stress according to Herz, together with the values of the friction coefficient Ud- Fig. 8 shows the basic geometry with contact points k ⁇ and mi, respectively, against the shaft 4 and the hub 5.
- a line F (dotted) between the contact points Ic 1 and mi, forms the angles ⁇ s and ⁇ h against the radii rs and rh, respectively. These angles are friction angles and are determined as before. The resulting forces of friction and normal forces will thereby act along the line F.
- the shapes of the contact surfaces are determined from criteria with basis in the friction angles ⁇ s and ⁇ h. These angles are primarily chosen to be constant and equal for all values of the radial play X. Secondarily, they are chosen to make the hub 5 self-centering in relation to the shaft 4, increasing with the play and with a variation about a 20 mean value of preferably ⁇ 30 %. Since the force equilibrium is determined by curvature radii, the play and the friction coefficient, normal forces result at different plays from an eccentricity between hub/shaft, which forces strive to eliminate the eccentricity, hi both these cases, the geometrical shape is achieved by application of usual mathematical calculation methods.
- the pressing together 3 A, 3B is advantageously made to be somewhat inclined (Fig. 12) and is larger at the outermost ends of the pins. A bevel is created thereby, which facilitates the mounting of the hub to the shaft.
- the inclination will also lead to the possibility to considerably decrease the contact pressure according to Herz, which has its maximum value at the ends of the pins.
- the inclination is performed to achieve a so called modified line contact.
- the cross-sectional dimension a is then reduced by a few percent at the outermost active portion of a pin 2, in order to be completely without reduction after an axial distance of about 2 times the dimension a.
- the contact sides of the pins against the shaft are made concave; i.e. the curvature radii rs become negative.
- the geometrical conditions will then lead to that rh should be chosen to be larger. Consequently, for contact points at the shaft as well as the hub, a considerably better and close contact is achieved which in turn increases the transmittable torque by the magnitude of a factor 3 under conditions that are otherwise the same.
- the elasticity of the strip 3A, 3B and thereby of the device 1 is large enough to enable that it is “endlessly” reeled up to form a roll and to enable it to easily be manually formed after the shape of a shaft 4.
- the minimum surface moment of inertia "I" for bending across the longitudinal direction L of the device in respect of the flexible elements, strips, at both sides of the device 1 should hence fulfil the requirement K (0.1 -a) 4 .
- the grooves 24 are preferably not symmetrically and centrally positioned at the ends of the pins 2. An initial prestressing of the pins 4 against the shaft 4 and hub 5, respectively, takes place by a non-symmetrical alternating positioning on every second pin. When the device 1 is assembled, all pins have a permanent slight bearing pressure against the shaft 4 and the hub 5, respectively. When double and opposing pins 2 are used with one pin intended for the driving in each direction of rotation, the grooves 24 are positioned obliquely at an angle ⁇ (Figs. 1OA and B).
- the grooves 24 are suitably alternately displaced, every second groove in a parallel direction outwards and every second groove in a parallel direction inwards, as seen in the radial direction in the assembled state between the shaft and the hub 5 (see Fig. 1).
- each pin 2 is in contact Ic 1 , k 2 with the shaft 4 and the hub 5 at or close to its end points.
- the pins 2 can be formed with a slight curvatiu ⁇ end 3 G in their longitudinal direction (Fig. 11), such that at least one contact point Ic 1 is achieved at the shaft 4 and one k 3 is ensured at the hub 5.
- the material on one side of the groove 24 is suitably made longer than necessary in the axial direction, such that it forms a protruding lower portion 201 intended to act as a assembly support.
- the strip 3 A, 3B may then slide against the protruding portion 201 and into the intended position.
- the protruding portion 201 can be removed.
- the extension 1' of the groove is longer man the width of the flexible element, whereby the latter will be locked and restrained by the protruding material.
- the axial length 1" or 1 of the force-transmitting portion 21 is advantageously made larger than 10 a.
- a soft transmission of the torque between the shaft 4 and hub 5 results, thus fulfilling the requirements that within German technology is referred to as "Kraft limp".
- the large length 1" of the force-transmitting portion 21 also ensures a safer transition from initial load to torque transmission.
- a large length ratio I/a compensates variations in radial play from geometrical flaws such as barrel shape or conicity.
- the length 1" of the force-transmitting portion 21 can advantageously be distributed over several shorter pins, the total axial length of which are to fulfill the criteria above.
- the friction coefficient ⁇ is a main parameter for the invention. It should be as large as possible and have a safe value the size of which is only limitedly affected by surrounding factors such as lubrication.
- the pins are given a rough surface that is achieved by chemical or mechanical influence (sand-blasting) or by a suitable coating such as carborundum or "Nylock Torque Patch” (Nylock Corporation, USA).
- the pin can be made to have slightly concave side surfaces 26, 27, which in some cases can be advantageous in order to achieve a good positioning (e.g. in connection with manufacturing) of the pins, since it is thereby possible to ensure that the outer portions at the respective corner zones 23 can form stops in a fixture e.g.
- Figs. 1OA and 1OB clarify that the groove 24 can be arranged to vary within the scope of the invention.
- Figs. IA and IB show an embodiment with "neutrally positioned pins" 2, in which the grooves 24 are positioned in a horizontal plane H (as seen in respect of the longitudinal extension of the coupling device 1 in a planar state) and at a displacement in relation to such a horizontal plane H, such that the groove 24 at one side of the coupling device 1 ends up closer to the upper surface 25 of the pin 2, while at the same side of the neighbouring pin 2 the groove 24 ends up closer to the lower surface 28.
- H seen in respect of the longitudinal extension of the coupling device 1 in a planar state
- FIG. 1OA an embodiment is shown with "opposed pins" 2, whereby the groove 24 can be obliquely arranged at an angle ⁇ in relation to said horizontal plane H and advantageously then such that it at one and the same side of the device 1 is downward inclined at the end of a first pin 2 and upward inclined at a neighbouring, second pin 2.
- Fig. 1OB the device 1 is shown in an unaffected state in which the elasticity of the strips 3 A, 3B makes them lie in one and the same plane, while Fig. 1 OA shows an effected state in which the pins have been forced to take positions with parallel side surfaces 26, 27, whereby the strips 3 A, 3B are bent.
- the groove 24 is thereby suitably given the same inclination ⁇ , with an extension in the same plane, at each end 2OA, 2OB of each pin 2.
- the groove 24 can be centrally arranged in height and hence at the same level at both ends and extending in the horizontal plane H.
- the strips 3 A, 3B are suitably arranged to have some prestressing (e.g. by bending), such that the elements position themselves as desired, e.g. in accordance with that described above.
- Figs. 13-15 show an alternative embodiment according to the invention, which e.g.
- a woven mat 2', 8 or a woven net is suitable for simpler constructions and makes use of a woven mat 2', 8 or a woven net.
- the specific property of a moment- transmitting woven mat is that the "thread" 2 in the moment-transmitting direction is of non-circular cross-section.
- the dimension of the thread can be very small ( ⁇ 1 mm), hi Fig. 14, the contact zones 25', 25" and the opposed ones 28', 28", respectively, at 2 ⁇ have for the sake of simplicity been drawn to be straight.
- the woven mat can be used as it is and be rolled about the shaft. It may also form "raw material" for the production of bushings by a process similar to the deep drawing/pressing of cans from planar sheets.
- Fig. 16 shows, as seen from above, an alternative embodiment of a device 1 according to the invention, in which flexible elements 3 A', 3B' that are integral with the pins 2 are used for the holding together (it should be here be noted that for the interpretation according to the claims of this patent application, the term holding together should be given a wide interpretation to comprise also a device in which the parts are integrated) of the pins 2.
- a device according to this embodiment is accordingly made in such a way that the same starting material is used to produce the pins 2 as well as the "strips" 3A', 3B', whereby the material that is used to act as a strip 3 A', 3B' is given a considerably smaller thickness of material than the pins 2, with the purpose of allowing adequate flexibility/elasticity.
- Fig. 17 shows a side view over another alternative embodiment, which shows that it is possible to use the principles according to the invention also without a continuous flexible element, in order to achieve a device 1 according to the invention.
- a flexible element 3C, 3D that gives the holding together of the pins 2 is instead formed by a male element 3C arranged at one side 27 of the pin 2 and a female element 3D, respectively arranged at the other side 26 of the pin, such that a long mat of pins 2 with flexible elements 3C, 3B them between can be formed.
- Figs. 18A, B show a shape of pins 2 intended for extremely large radial plays X.
- the contact zones comprise practically the entire cross-section or between lines F 1 and F 2 (25", 28") and the corresponding for the opposed direction of rotation (25 1 , 28").
- the width b can be larger than the dimension a.
- the width b and the dimension amax can be identical and even coinciding with the maximum dimension c of the pin.
- the dimension b is a dimension that is chosen to be representative for the cross-sectional shape in question.
- Figs. 19 A, B illustrate pins 2 according to Fig.
- pins 2 that are provided with a recess with a surface of rotation in the form of a circular peg 29 (or a circular groove or the corresponding), in order for the holding together with a articulate/bent element 3 A", 3B", here in the form of a strip with integral sleeves 30 adapted to the pegs 29 (Fig. 20), or in the form of double strips (not shown) wrapped together about the pegs 29 of the pins, or in the form of threads twisted in pairs (not shown).
- a required initial bearing against the shaft and the hub can be achieved by slightly bent pins according to the above, and/or a displaced positioning of the pegs 29.
- the invention can be varied in its widest sense within the idea that forms the basis of the invention.
- the pins may hence be alternately positioned in groups of two, three, four and so on, pins in each group.
- alternative elements instead of strip shaped
- a wire of suitable flexibility/elasticity or a plurality of wires in arrangements diagonally or endlessly as a sine curve e.g. made in spring steel, or some other suitable elastic metal/alloy, suitable polymer or combinations thereof, may be used.
- the term flexible also means articulated (Figs. 17, 18).
- the invention can furthermore be used also when the pins 2 are applied at a strip 3 A, 3B in some other way than that described above, e.g. a strip or strips in the form of a wire that penetrates holes in the pin, etc., and that combinations of different types of strips/wires can be used in a device, such as strips on one side and wires on the other side. It is also realised that in certain applications, it is adequate with a strip 3 A arranged on one side and that as an alternative it can be mounted in a central groove.
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Mechanical Operated Clutches (AREA)
- Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)
- Transmission Devices (AREA)
- Snaps, Bayonet Connections, Set Pins, And Snap Rings (AREA)
- One-Way And Automatic Clutches, And Combinations Of Different Clutches (AREA)
- Transmissions By Endless Flexible Members (AREA)
Abstract
Description
Claims
Priority Applications (5)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2009538368A JP5327747B2 (en) | 2006-11-28 | 2007-10-22 | Torque transmission method and device for coupling hub and shaft together |
US12/094,182 US8151960B2 (en) | 2006-11-28 | 2007-10-22 | Method and device for torque transmission |
KR1020097006539A KR101395247B1 (en) | 2006-11-28 | 2007-10-22 | Method and device for torque transmission |
EP07835348.9A EP2265836A4 (en) | 2006-11-28 | 2007-10-22 | Metod and device for coupling together a hub and a shaft |
DE112007000105T DE112007000105T5 (en) | 2006-11-28 | 2007-10-22 | Method and device for torque transmission |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
SE0602539-9 | 2006-11-28 | ||
SE0602539A SE530580C2 (en) | 2006-11-28 | 2006-11-28 | Method and apparatus for connecting a hub with a shaft |
Publications (2)
Publication Number | Publication Date |
---|---|
WO2008066469A1 true WO2008066469A1 (en) | 2008-06-05 |
WO2008066469A8 WO2008066469A8 (en) | 2008-09-04 |
Family
ID=39468165
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/SE2007/050763 WO2008066469A1 (en) | 2006-11-28 | 2007-10-22 | Method and device for torque transmission |
Country Status (8)
Country | Link |
---|---|
US (1) | US8151960B2 (en) |
EP (1) | EP2265836A4 (en) |
JP (1) | JP5327747B2 (en) |
KR (1) | KR101395247B1 (en) |
DE (1) | DE112007000105T5 (en) |
RU (1) | RU2009103311A (en) |
SE (1) | SE530580C2 (en) |
WO (1) | WO2008066469A1 (en) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2010063249A3 (en) * | 2008-12-01 | 2010-08-05 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Freewheel for a crank-cvt transmission |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE112017004972T5 (en) * | 2016-09-30 | 2019-06-19 | Denso Corporation | Clutch and engine |
Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB859664A (en) * | 1957-04-08 | 1961-01-25 | Borg Warner | Sprag |
US4809831A (en) * | 1986-06-20 | 1989-03-07 | Nsk-Warner K. K. | One-way sprag clutch and assembly method of sprags in retainer |
US4960189A (en) * | 1987-12-08 | 1990-10-02 | Nsk-Warner Kabushiki Kaisha | Serpentine-shaped sprag retainer of a sprag-synchronized one-way clutch |
Family Cites Families (14)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2881886A (en) * | 1954-11-01 | 1959-04-14 | Borg Warner | One-way clutches |
US2954855A (en) * | 1957-11-25 | 1960-10-04 | Formsprag Co | Energizing means for one-way clutches of the sprag type |
US3017210A (en) * | 1958-04-07 | 1962-01-16 | Borg Warner | Non-rotating sprag coupling |
FR1407704A (en) | 1964-06-17 | 1965-08-06 | Peugeot Et Cie Sa | Strip intended to provide rotating securing elements between two concentric parts, elements obtained from this strip and assemblies made |
CH473330A (en) | 1965-12-30 | 1969-05-31 | Titt Georg | Device for the transmission of torques and method for producing this device |
US4569614A (en) | 1982-06-30 | 1986-02-11 | Yukio Yamauchi | Coupling |
US5025902A (en) * | 1990-01-04 | 1991-06-25 | Aichi Kikai Kogyo Kabushiki Kaisha | Bidirectional differential clutch |
JP2975133B2 (en) * | 1990-01-31 | 1999-11-10 | エヌティエヌ株式会社 | Rotation transmission device |
DE9014391U1 (en) * | 1990-10-17 | 1991-01-03 | Grothe, Hermann, 5630 Remscheid, De | |
WO1992014074A1 (en) * | 1991-01-30 | 1992-08-20 | Ntn Corporation | Rotation transmitting device |
JP3547859B2 (en) * | 1995-07-14 | 2004-07-28 | 愛知機械工業株式会社 | Two-way differential clutch |
DE60010536T2 (en) * | 1999-01-28 | 2004-09-30 | Aichi Kikai Kogyo K.K. | Two-way differential clutch |
SE518695C2 (en) * | 2001-03-22 | 2002-11-05 | Rolls Royce Ab | Shaft coupling and shaft joint with a first shaft part, a second shaft part and a shaft coupling |
JP4813036B2 (en) * | 2004-10-04 | 2011-11-09 | Nskワーナー株式会社 | One-way clutch and sprag for one-way clutch |
-
2006
- 2006-11-28 SE SE0602539A patent/SE530580C2/en not_active IP Right Cessation
-
2007
- 2007-10-22 RU RU2009103311/11A patent/RU2009103311A/en not_active Application Discontinuation
- 2007-10-22 US US12/094,182 patent/US8151960B2/en not_active Expired - Fee Related
- 2007-10-22 KR KR1020097006539A patent/KR101395247B1/en not_active IP Right Cessation
- 2007-10-22 JP JP2009538368A patent/JP5327747B2/en not_active Expired - Fee Related
- 2007-10-22 DE DE112007000105T patent/DE112007000105T5/en not_active Withdrawn
- 2007-10-22 EP EP07835348.9A patent/EP2265836A4/en not_active Withdrawn
- 2007-10-22 WO PCT/SE2007/050763 patent/WO2008066469A1/en active Application Filing
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB859664A (en) * | 1957-04-08 | 1961-01-25 | Borg Warner | Sprag |
US4809831A (en) * | 1986-06-20 | 1989-03-07 | Nsk-Warner K. K. | One-way sprag clutch and assembly method of sprags in retainer |
US4960189A (en) * | 1987-12-08 | 1990-10-02 | Nsk-Warner Kabushiki Kaisha | Serpentine-shaped sprag retainer of a sprag-synchronized one-way clutch |
Non-Patent Citations (1)
Title |
---|
See also references of EP2265836A4 * |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2010063249A3 (en) * | 2008-12-01 | 2010-08-05 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Freewheel for a crank-cvt transmission |
JP2012510594A (en) * | 2008-12-01 | 2012-05-10 | シェフラー テクノロジーズ ゲゼルシャフト ミット ベシュレンクテル ハフツング ウント コンパニー コマンディートゲゼルシャフト | Freewheel used in crank CVT transmission |
US9133897B2 (en) | 2008-12-01 | 2015-09-15 | Schaeffler Technologies AG & Co. KG | Freewheel for a crank-CVT transmission |
Also Published As
Publication number | Publication date |
---|---|
US8151960B2 (en) | 2012-04-10 |
JP2010511128A (en) | 2010-04-08 |
JP5327747B2 (en) | 2013-10-30 |
KR20090083333A (en) | 2009-08-03 |
EP2265836A2 (en) | 2010-12-29 |
DE112007000105T5 (en) | 2008-10-23 |
KR101395247B1 (en) | 2014-05-27 |
RU2009103311A (en) | 2010-10-10 |
SE0602539L (en) | 2008-05-29 |
EP2265836A4 (en) | 2013-07-17 |
WO2008066469A8 (en) | 2008-09-04 |
US20100219033A1 (en) | 2010-09-02 |
SE530580C2 (en) | 2008-07-08 |
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