WO2006108378A1 - Laschenkette mit konvex-konkavem kontakt der wiegestücke - Google Patents
Laschenkette mit konvex-konkavem kontakt der wiegestücke Download PDFInfo
- Publication number
- WO2006108378A1 WO2006108378A1 PCT/DE2006/000523 DE2006000523W WO2006108378A1 WO 2006108378 A1 WO2006108378 A1 WO 2006108378A1 DE 2006000523 W DE2006000523 W DE 2006000523W WO 2006108378 A1 WO2006108378 A1 WO 2006108378A1
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- WO
- WIPO (PCT)
- Prior art keywords
- rocker
- tabs
- rolling
- chain according
- profiles
- Prior art date
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Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16G—BELTS, CABLES, OR ROPES, PREDOMINANTLY USED FOR DRIVING PURPOSES; CHAINS; FITTINGS PREDOMINANTLY USED THEREFOR
- F16G5/00—V-belts, i.e. belts of tapered cross-section
- F16G5/16—V-belts, i.e. belts of tapered cross-section consisting of several parts
- F16G5/18—V-belts, i.e. belts of tapered cross-section consisting of several parts in the form of links
Definitions
- the present invention relates to a link chain of a plurality of tabs, which are each interconnected by a hinge comprising at least one piece of rocker.
- Tab chains are known in a wide variety of designs, e.g. from DE 38 26 809 with further references or DE 30 27 834, in the various associations are shown.
- EP 0 800 018 also describes a continuously variable bevel gear transmission in which such plate link chains can be used.
- the joint pieces connecting the individual links are formed as pairs of rocker, which transmit the frictional forces between the conical disks and the link chain and which are inserted into the recesses of the tabs.
- the cradles have surfaces facing each other, which roll on each other in the intended use.
- the cradles are shaped so that the rolling profiles are centroids.
- Object of the present invention is to increase the carrying capacity of such a link chain, ie in particular the transferable tensile forces further. Furthermore, the noise emission during operation should be reduced.
- This problem is solved by a link chain of a plurality of tabs, each connected by a hinge comprising at least one rocker, which can roll with a Wälzprofil on a mating tab associated Wälzprofil, wherein the rocker at at least two other points with the mating tab is in contact and the surface contours of the mating tab and the rocker are in a region around the contact points (K, K 1 ) reciprocally enveloping curves, wherein one of the rolling profiles is concave and one of the rolling profiles is convex.
- tabs are arranged on both sides. In order to be able to differentiate these tabs, which individually may be identical components, for purposes of the present patent application, these are referred to herein as tabs and counter tabs. If a joint is cut in a two-composite of a link chain, then the tabs projecting in one direction are designated as those which designate tabs projecting in the other direction as counter-tabs. If one were to cut an adjacent joint, the names would be reversed from the perspective of the previously considered tab. Thus, in the context of the present application, the terms tab and mating tab are merely to refer to different tab functions with respect to a single hinge.
- the tabs Under load piece is here understood in a known manner, in particular a bolt which is part of the joint and a plurality of tabs in the transverse direction of the chain, the tabs form a chain link, interconnecting.
- the Wälzprofil the rocker or the rocker and the counter-tab associated Wälzprofil may have any contour, for example, circular or parabolic. Under one of the counter-tab associated Wälzprofil is understood that this is applied either directly to the tab or as firmly connected to the links forming a chain link in the manner of a rocker. Under contact standing of the rocker with at least two other points of the mating tab is understood here that these are sliding or rolling or both at the same time flat or point or line in contact.
- this will be a point-like contact in a two-dimensional representation and a linear one in a three-dimensional representation.
- the wording "in an area around the contact points" is intended to express that the contact points in normal operation of the chain, in which a deflection of the chain links against each other should take place up to a predetermined value, the contact points against each other and slide on only within a certain range So if you have an undefended chain, the contact point at a certain place. In contrast, in the case of a chain which is deflected to the maximum extent on both sides, this contact point will lie at a different location. Outside these ranges, in which the contact points come to lie, one of the kinematic conditions shown here deviating geometry can be selected.
- the enveloping curves of these involutes describe a kinematically acceptable solution.
- An example of such a kinematic compatible solution is, for example, if the weight piece is designed as involute in the intended contact area, so that the contact area of the flap directly results in a reciprocal involute. Both curves are already involute in themselves, so that the group of curves that perform different points on the involute with relative rolling of the rolling profiles, give the same identical involute.
- the reciprocal enveloping curves are respectively involutes of the pitch profiles associated with the base circles or envelope of an involute crowd by surface points of the counter-flap or the rocker.
- the rolling profile of the rocker is convex and that the counter-blade associated rolling profile is concave or that the rolling profile of the rocker is concave and the counter-blade associated rolling profile is convex.
- the contact between the pins is convex-concave (involute internal engagement) or convex-convex (involute external engagement).
- the convex-concave contact leads to smaller Hertzian stresses at the same curvature of the convex cradles - A -
- the counter-flap is associated with a further weight piece.
- the (first) weighing piece does not roll off directly on the counter-plates, but instead on another weighing piece which connects the counter-plates with each other.
- the rocker is firmly connected to the tab and the other rocker is firmly connected to the counter-flap.
- a plate chain of a plurality of tabs which are each connected by at least one rocker, wherein the rocker can slide with a Wälzprofil on one of the mating tab associated Wälzprofil and the Wälzprofil at least two points with the Wälzprofil the counter-tab is in contact, wherein the surface contours of the Wälzprofile in a region around the contact points reciprocally enveloping curves.
- a common normal of the contour of the rolling profiles in the contact points passes through the instantaneous rotary pole.
- the geometry of all interacting bodies is thus kinematically compatible with their movement, there is no undercutting, which would cause a deformation of the body.
- one of the rolling profiles is concave and the other of the rolling profiles is convex. This reduces the Hertzian surface pressure at the contact points.
- rocker is firmly connected to any of the tabs and that both tabs have rolling profiles on which rolling profiles of the rocker piece can roll or slide.
- the free-floating rocker pin kinematically interacts with the remaining parts only by means of rolling and sliding movements, slipping out in the axial direction of the rocker, which is equivalent to a direction transverse to the axial direction (direction of movement) of the chain as such
- These guides are used to make the bevel gears in a bevel gear, whereby no guidance takes place between the bevel gears.
- the rolling profiles are arranged on to the respective lugs fixedly connected rocking pieces.
- the weighing pieces can also be firmly connected to one of the tabs. In this case, slide or roll firmly connected to a lug weighing piece on directly introduced into the tabs Wälzprofilen or on another Wälzprofil, which also connects several tabs together to form a chain link.
- both rolling profiles of the rocker piece are convex and the rolling profiles of the rocker pieces of the lugs are concave. It can also be provided that both rolling profiles of the rocker are concave and the rolling profiles of the rocker arms of the straps are convex. So it rolls in each case a concave with a convex profile. This can also be achieved if one of the profiles of the rocker is concave and the associated profile of the straps is convex, the other profile of the rocker is convex and the associated profile of the straps is concave.
- rocker with two tabs is in sliding contact at two points and can roll on both Wälzprofilen at one point.
- the rocker is in sliding contact with two Wälzprofilen at two points.
- the tabs can be embraced by the cradles.
- two opposing pieces of rock are preferably firmly connected to each other.
- link chain comprising a multiplicity of lugs, which are connected to one another by lugs in order to form links, the lugs engaging around the lugs.
- a link chain can be any geometric or
- the surface contours of the tab and the rocker in a region around the contact points reciprocally enveloping curves and one of the rolling profiles are concave and one of the rolling profiles is convex.
- the rolling profiles of the straps are concave and the rolling profiles of the rocker pieces are convex.
- the rolling profiles of the flaps are convex and the rolling profiles of the rocking pieces are concave.
- FIG. 1a is a sketch of tabs and cradles of a hinge of a tab chain
- Figure 1 is a schematic representation of the geometry and kinematics of a joint of a link chain.
- Figure 2 is a schematic representation of the kinematics of a hinge of a link chain in relatively deflected chain links.
- Fig. 3 shows an alternative embodiment with only one piece of rocker within the joint
- Figure 5 is a joint with floating pin as a rocking piece.
- Fig. 6 a part of a chain with a plurality of tabs and joints gem.
- FIG. 7 shows a joint with a sliding weight piece
- Fig. 8 a part of a chain with a plurality of tabs and joints gem.
- Fig. 10 a part of a chain with a plurality of tabs and joints gem.
- FIGS. 15 and 16 show an embodiment of a joint with cradles embracing the tabs
- FIGS. 17 and 18 show a further embodiment of a joint with cradles which embrace the tabs.
- FIG. 1 and Fig. 1a show a section of a link chain.
- auxiliary lines as well as large parts of the designations have been suppressed for the sake of clarity, otherwise the illustrated article corresponds to FIG. 1.
- Shown is a tab L1 and a tab L2.
- a link chain consists of a plurality of packet-like laminated tabs, as described for example in DE 3027834. Different arrangements, e.g. the two- or three-lobe bandage, possible.
- the execution of the joint of importance therefore, only two hingedly interconnected tabs in the region of the joint are shown in Fig. 1.
- the joint comprises two pieces W1 and W2.
- FIG. 1 shows a section of a link chain.
- auxiliary lines as well as large parts of the designations have been suppressed for the sake of clarity, otherwise the illustrated article corresponds to FIG. 1.
- Shown is a tab L1 and a tab L2.
- a link chain consists of a plurality of packet-like laminated tabs,
- the bars are marked with hatchings of different orientation, areas in which the hatches overlap are areas in which the flap in the front overlaps the rear.
- the rocker pieces are each firmly connected to a lug, here, the weight piece W1 is connected to the tab L1 and the weight piece W2 to the tab L2.
- the cradles connect several tabs of the link chain together, but this is not shown here.
- the cradles roll on rolling profiles (w1) and (w2) from each other. In the present example, the rolling profiles are circular cut-outs, but it could also be cutouts of ellipses, parabolas or the like.
- the engagement line (g) is tangent in A and E to the basic circuits (gl) and (g2) and contains the instantaneous center of rotation C of the relative movement of the Wälzprofile.
- a point K of the engagement line describes the involutes (e1) and (e2) during the rolling motion on the base circles. Both involutes are in contact at point K.
- the lugs L1 and L2 are fixedly connected to the cradles by the fastening profiles M1-R1-S1 and R2-S2.
- An involute arc M1-K-N1 of the involute (e1) is formed on the weight piece W1 as a guide profile.
- a conjugate guide profile, Involute involute arc M2-K-N2 (e2), is formed on tab L2.
- the involute (e1) arises in thought by the rolling of the rocker W1 on According to the retained weight piece W2, the involute (e2) is created by rolling the weight piece W2 on the weight piece W1.
- the involutes are therefore reciprocal to each other.
- the connection profile P1-N1 establishes the connection between the guide profile and the rolling profile of the rocker W1, while the connection profile P2-R2 establishes the connection between the rolling and fastening profile of the rocker W2. In the connection points, the two profiles have a common tangent.
- the connection profiles can be arbitrarily formed by different curves and straight lines, according to geometric, kinematic and strength criteria.
- the rocker W1 In order to provide a complete and kinematically compatible guidance of the rocker W1 relative to the rocker W2 and its tab L2, the rocker W1 must be supported in three points. Therefore, the whole described geometry is copied symmetrically to the axis 01-02. The cradle W1 will then be in contact with the cradle W2 and its tongue L2 at points K, C and K '.
- the cradles W1 and W2 Upon rotation of the tab L1 with respect to the tab L2, the cradles W1 and W2 roll on their pitch profiles (W1) and (W2). From the perspective of Wälzprofils W1 and the associated tab L1, the Wälzprofil (W1) Polkurve or Gangpolbahn, so the location of the currently rotating poles at different angles of the tabs to each other, according to the Wälzprofil (W2) Polkurve or Gangpolbahn from the perspective of the tab L2 or of the weight piece W2.
- the rocker W1 and W2 do not slide, but always roll off each other, so that only one rolling motion and no sliding movement of the two rocker pieces relative to each other arises. In the embodiment of Fig. 2, the rocker member W1 always.
- the contour of the rocker W1 about the contact point K or K 1 is an involute to the base circle (g2) of the rocker W2.
- the surface contour of the tab L1 in the region around the contact points K or K ' is an involute to the base circle (g1) of the cradle W2.
- This has the consequence that a normal to the (common) tangent of both involutes in the contact point K or K 'always goes through the instantaneous center of rotation C.
- the involute profiles M1-K-N1 of the cradle W1 and M2-K-N2 of the flap L2 form an involute internal engagement, the rolling circles of which are the rolling profiles (W1) and (W2) of the cradles are (thus the distances C-P1 and C-P2).
- the thickness and width of the cradles, the strength and shape of the tabs, the fastening profiles between the cradles and tabs are determined by strength, acoustics, material selection and other criteria.
- any relative position of the chain links is shown in FIG. If the wedge piece W2 is dispensed with, the tab L2 can directly contain the rolling profile and engage directly with the weight piece W1 (FIG. 3).
- Fig. 3 shows an alternative embodiment, in which the weighing piece W2 is missing, so that the flap L2 directly has the rolling profile (W2). The tab L2 is thus in direct engagement with the weight piece W1.
- the rolling profile (W1) is convex
- the rolling profile (W2) is concave.
- it is an engagement of a convex with a concave profile, so that there is an extrapolar involute internal engagement.
- Several linked chain links are shown in Fig. 4.
- the relative movement of the rocker is a pure rolling motion (rolling without sliding).
- the rocker points are in contact at the instantaneous turning point C.
- the common norm of the involutes at the contact point K is always the line of action and contains the instantaneous pole C in every relative position. This is a prerequisite for a kinematically compatible centroidal movement between the chain links of the chain.
- this engagement transmits the forces between the rocker W1, W2.
- conical disks of a conical disk gear can be in contact between the pins and their brackets forces arise whose resulting force has a different direction than the common normal in the instantaneous rotation C.
- the components are transmitted in the direction of the normal at the contact point C, the others Components are transmitted at the contact points K, K 'of the involutes.
- the kinematic geometry of the chain link is an extrapolar involute inner and outer engagement presented.
- a floating "floating-pin" floats between two other cradles whose flaps carry the cantilevered cradle, which provides several kinematic benefits and can also provide acoustic enhancements.
- Fig. 5 explains the structure of the joint.
- a cantilevered rocker W1 which is firmly connected as a "floating pin" with none of the tabs on two firmly connected to each one of the tabs L2, L2 1 Wiegge W2 and W2 ⁇ Um analogies to
- the circular arcs C-P1 and C-P2 form the rolling circles (w1) with the center 01 and (w2) with the center 02
- the pitch curves of the rocker arms W1 and W2 ( Figure 1)
- the pitch circles may be tangent on the inside or outside, that is, they may form an internal or external involute engagement
- the engagement line (g) is tangent to A and E to the pitch circles (g1) and (g2) and contains the instantaneous rotational pole C of the relative movement of the rolling profiles
- a point K of the engagement line describes the involutes (
- the two involutes are in contact at point K.
- the flap L2 is firmly bound by the fastening profile R2-S2.
- An involute arc M1-K-N1 of the involute (e1) is formed on the weight piece W1 as a guide profile.
- the involute arc M2-K-N2 of the involute (e2) forms a guide profile of the flap L2.
- the connection profile P2-R2 establishes the connection between the rolling and fastening profile of the weight piece W2. In the connection points, the two profiles have a common tangent.
- the connection profile can be arbitrarily formed by different curves and straight lines, according to geometric, kinematic and strength criteria.
- the rocker W1 In order to provide a complete and kinematically acceptable guidance of the rocker W1 relative to the rocker W2 and its tab L2, the rocker W1 must be supported in three points. Therefore, the whole described geometry is copied symmetrically to the axis O1-O2. The cradle W1 will then be in contact with the cradle W2 and its tab L2 at points K, C and Ka.
- the involute profiles M1-K-N1 of the rocker W1 and M2-K-N2 of the tab L2 form an extrapolar involute internal or involute outer engagement, the rolling circles of which Wälzprofile C-P1 and C-P2 of the rocker pieces are.
- the thickness and width of the cradles, the strength and shape of the tabs, the fastening profiles between the cradles and tabs are determined by strength, acoustics, technology and other criteria.
- the rolling profile C-P1 and the guide profile M1-K-N1 of the rocker W1 are symmetrically copied around an axis of symmetry (xx) perpendicular to 01-02 and become rolling profile C-PV and guide profile C'-M'-K'-NI 1 ,
- the profile N1-N1 'of the rocker W1 can be designed as a connection profile arbitrary.
- a flap L2 'with its own weight piece W2' corresponds to a symmetrical representation about the axis (xx) of the flap L2 and its weight piece W2.
- the two tabs L2 and L2 'with the associated rocker W2 and W2 1 form with the cantilever mounted rocker W1 (floating-pin) a double joint.
- Each lug with its rocker forms with the rocker W1 a joint in which the relative movements Zentroidalterrorismen (rolling movements along the circular Rastpolbahn here) and thus the aforementioned conditions of kinematic geometry are met.
- the rocker W1 hovers between the rocker W2 and W2 'with their tabs L2 and L2', it is called a floating pin.
- In contact with conical disks of a continuously variable transmission can come all three rocker or only the weight piece W1.
- the axial movements of the rocker W1, W2 and W2 'but must be limited in any case.
- Several linked chain links are shown in Fig.
- the rocker W1 is in each case in two places with two tabs in engagement, these are the points K, K 1 , Ka and Ka. 1
- the above-mentioned, normal tangents in these points also pass through the instantaneous center point C or C, respectively.
- the weighing piece W1 rolls on the weighing pieces W2 and W2 1 at points C and C, respectively, at points K, K '.
- Ka and Ka 1 is a pure sliding movement of the tabs on the cradle W1 instead.
- the tabs L2 and L2 1 can directly (analogous to the embodiment shown with reference to FIG. 3) contain the rolling profiles of the rocker pieces and roll directly on the weight piece W1.
- the racks are in contact at the momentary turning poles C and C.
- the common normals of the involutes at the point of contact are always the lines of action and in each relative position contain the engaging poles C and C.
- the joint is actually a double joint between two adjacent chain links (tabs), this results in a larger angle between two adjacent tabs and reduces a negative poligonal effect.
- the tabs L2 and L2' can contain the active profiles of the cradles and engage directly with the cradle W1.
- the tabs can be kept shorter and the negative effects of the poligonal effect are further reduced.
- the point of application of the force between the pins in contact is the contact point of the rolling profiles and migrates on the rolling profiles. The migration of this point is smaller at the convex-convex contact.
- the cantilevered rocker has good bending strength and buckling stability.
- the Floating-Pin (Floating-Wiege GmbH) floats between two conjugate rocker pieces that roll on the Wälzprofilen and in the tabs it is guided.
- the Poligonal bin can be further improved by dispense with the pins W2 and W2 ', the tabs come directly into contact with the floating pin.
- the tabs are shorter and thus the distance between two adjacent joints is also shorter. The distances between two adjacent joints are smaller and thus better acoustic characteristics can be expected.
- the three rocker joints of the joint can be used to increase the transmittable torque of a CVT transmission because they have higher buckling and bending strength.
- the contact point migration is greater than in the involute external engagement. This disadvantage can be compensated (at least in part) with a smaller radius of curvature of the weight piece.
- FIGS. 7 and 8 show a further alternative embodiment of a link chain according to the invention.
- the cradles are able to fix the chain links against each other both in the direction of movement of the chain (axially) and perpendicular thereto. In this embodiment, therefore, it is not necessary that the rocker pieces directly transmit a force to the tabs.
- an involute internal engagement is presented as the kinematic geometry of the chain link.
- Fig. 7 illustrates the structure of another embodiment of the joint.
- the rolling circles (w1) with the center 01 and (w2) with the center 02 have a common tangent at the point C. They represent the centroids of the relative movement.
- the engagement line (g) is tangent in A and E at the base circles (gl) and (g2) and contains the instantaneous center of rotation C of the relative movement of the centroids.
- a point K of the action line describes the involutes (e1) and (e2) during their rolling motion on the base circles. The two involutes are in contact in K. With the cradles W1 and W2, the tabs L1 and L2 are fixedly connected by the fastening profiles R1-S1 and R2-S2.
- connection profiles P1-K-T1 of the involute (e1) and P2-K-T2 of the involute (e2) are arranged as active profiles.
- the connection profiles P1-R1 and P2-R2 are the connection between the active profiles and fastening profiles of the legs W1 and W2.
- the connection profiles can be arbitrarily formed by different curves and straight lines, according to geometric, kinematic and strength criteria. In the connection points, the two profiles have a common tangent.
- the whole described geometry is copied symmetrically to the axis 01-02.
- the cradle W1 is then in contact with the cradle W2 and its tongue L2 at points K and K '.
- the involute profiles P1-K-T1 of the rocker W1 and P2-K-T2 of the rocker W2 form an involute internal engagement whose rolling circles (w1) and (w2) are virtual centroids of the relative movement.
- Several linked chain links are shown in FIG.
- a tab can contain the active profile and intervene directly with the conjugate piece. This can lead to smaller dimensions of the joint and reduce the negative effect of the poligonal effect.
- the relative movement of the rocker pieces theoretically represents a pure rolling motion (rolling without sliding) of the unembedded rolling circles (w1) and (w2). In reality, the rocker pieces roll and slide reciprocally on the active profiles during the rolling motion of the rolling circles.
- the cradles are always in contact in two points, namely K and K '.
- the common normal of the involutes in the contact point K or K J is always the line of action and contains in each relative position the instantaneous rotation pole (engagement pole) C.
- the forces between the involutes in the contact points K and K 1 are in the direction of the engagement lines CK and CK 1 ü - transferred. Because of the sliding movement between the active profiles of the cradles, frictional forces will also arise at points K and K 1 .
- the pressure angle ⁇ is important for the friction forces and the stability of the joint with respect to the inclination of the relative rotational movement of the rocker teeth about the 01-02 axis.
- the joint has an efficiency comparable to that of the involute intervention.
- Fig. 9 illustrates the structure of another embodiment of the joint.
- the rolling circles (w1) with the center 01 and (w2) with the center 02 have a common tangent at point C. They represent the centroids of the relative movement.
- the engagement line (g) is tangent in A and E at the base circles (gl) and (g2) and contains the instantaneous center of rotation C of the relative movement of the centroids.
- a point K of the action line describes the involutes (e1) and (e2) during their rolling motion on the base circles. The two involutes are in contact in K.
- the involute arches P1-K-T1 of the involute (e1) and P2-K-T2 of the involute (e2) are embodied as active profiles on the rocker arms W1 and W2.
- the active profile P2-K-T2 of the rocker W2 is connected to the mounting profile R2-S2 through the connection profile P2-R2.
- the profiles have a common normal in the connection points.
- the involute profiles P1-K-T1 of the rocker W1 and P2-K-T2 of the rocker W2 form an involute internal engagement whose rolling circles (w1) and (w2) are virtual centroids of the relative movement.
- the attachment and connection profiles can be arbitrarily formed by different curves and straight lines, according to geometric, kinematic and strength criteria.
- an axis of symmetry (x-x) between the selected active profiles and the instantaneous center of rotation C is selected. If the symmetry axis contains the instantaneous turning pole, this can lead to advantageous kinematic and dynamic properties.
- the profile P1-K-T1 and its symmetrical profile P1'-K'-TT represent the active profiles of the same load piece and are connected to a connection profile P1-P1 'of any shape.
- Symmetrical mirrored profiles of the cradle W2 represent the profiles of the cradle W2', which comes into contact with the active profile of the cradle W1 in K '.
- the weight piece W1 also floats here suspended between the pins W2 and W2 '.
- the whole described geometry is copied around the axis 01 -02.
- the common normals of the involutes in the contact points K, K ', Ka and Ka ' are always the lines of action and contain the engaging pole (instantaneous turning point) C in each relative position.
- the forces between the involutes in the contact points are transmitted in the direction of the engagement lines. Due to the sliding movement between the active profiles of the pins, frictional forces also arise in the contact points.
- the pressure angle ⁇ is important for the friction forces and the stability of the joint with respect to the inclination of the relative rotational movement of the rocker pieces. Also, this joint has an efficiency comparable to that of the involute intervention.
- FIGS. 11 to 14 explain the construction of a further embodiment of the joint.
- the rolling circles (w1) with the center 01 and (w2) with the center 02, innentangent at the point C, represent the rolling circles of the relative movement (Fig. 11).
- the engagement line (g) is in A and E tangent to the basic circuits (gl) and (g2) and contains the instantaneous rotation C of the relative movement of the rolling circles.
- a point K of the action line describes the involutes (e1) and (e2) during their rolling motion on the base circles.
- the two involutes are in contact at point K.
- Segments of two involute gearwheels of the involute intermeshing are the bodies Z1 and Z2. Another symmetrical engagement with the gears Z1 'and Z2' is shown in FIG.
- the symmetry axis is perpendicular to the line 01-02 and outside the point of intersection of the involute (e2) with the axis 01-02.
- the involute arches P1-K-T1 of the involute (e1) and P2-K-T2 of the involute (e2) are designed as active profiles on the rocker arms W1 and W2.
- the active profile P2-K-T2 of the rocker W2 is connected to the active profile P2'-K'-T2 'by the connection profile P2-R2-R2'-P2'.
- the active profiles of the cradles W1 and W1 ' are connected to the fastening profiles R1-S1 and R1'-S1' by the connection profiles P1-R1 and P1'-R1 '.
- the profiles in the connection points have a common normal.
- the involute profiles P1-K-T1 of the rocker W1 and P2-K-T2 of the rocker W2 form an involute internal engagement whose rolling circles (w1) and (w2) are virtual centroids of the relative movement.
- the thickness and width of the cradles, the strength and shape of the tabs, the fastening profiles between the cradles and tabs are determined by strength, acoustics, technology and other criteria.
- the fastening and connection profiles can be arbitrarily formed from different curves and straight lines, according to geometric, kinematic and strength criteria. The same geometry, the load pieces W2 and W1 1 on.
- the symmetrical profiles of the cradle W1, T1 '-K'-P1' -R1 '-S1' represent the profiles of the cradle W1 ', which comes into contact with the active profile of the cradle W2 at point K'.
- the rocker W2 is called a floating pin because it is fixedly connected to no element and floats between the rocker W1 and WT.
- the rocker W2 is called a floating pin because it is fixedly connected to no element and floats between the rocker W1 and WT.
- the relative movement of the rocker pieces theoretically represents a pure rolling motion (rolling without sliding) of the rolling circles (w1) and (w2), which themselves do not find a correspondence on the surface of one of the components.
- the rocker bars roll and slide reciprocally on the active profiles during the rolling motion of the rolling circles.
- the rocker W1 (the floating pin) is always in contact with the rocker W2 in two points K and Ka and with the rocker W2 'also in two points K' and Ka '.
- the common normals of the involutes in the contact points K, K ', Ka and Ka' are always the lines of engagement and contain the engagement pole (instantaneous rotation) C in each relative position.
- the forces between the involutes in the contact points are transmitted in the direction of the engagement lines.
- the pressure angle ⁇ (Greek alpha) is important for the friction forces and the stability of the joint with respect to the inclination of the relative rotational movement of the rocker teeth about the 01-02 axis.
- the joint has an efficiency comparable to the efficiency of involute engagement.
- FIGS. 15 and 16 explain the construction of a further embodiment of the joint.
- the centroidal mean pitch curves are the circle (w1) with the center 01 and the pitch line (w2), both having a common tangent (tangent) at point C ( Figure 15).
- the engagement line (g) is tangent in A at the base circle (gl) and contains the instantaneous rotation C of the relative movement of the pitch circle (w1) and the rolling line (w2).
- a point K of the engagement line describes the involute (e1) during its rolling motion on the base circle. Together with the intervention line and vertically in point K, a generating line (gg) is considered.
- the nerierstraight (gg) the same involute (e1).
- the involute (e1) and the generating line (g- g) are thus reciprocal enveloping curves.
- the two reciprocal enveloping curves are in contact at point K.
- the weighing piece W1 is designed so that it contains the generating line as an active profile.
- the involute (e1) and the active profile of the cradle are copied symmetrically along the axis 01-C. This results in the profiles (gg 1 ) and (e1 ').
- the tab L1 comprises the two involute profiles of the engagement and the cradle the two generation lines.
- the left profile of the tab, the curves (11) and (H ') are designed so that they do not collide with the weight.
- Symmetrically to (w2) the profile of the weight piece is copied so that it gets the whole shape as shown in FIG.
- the balance piece has two symmetry axes, namely (w2) and 01-C.
- the flap has the profiles (e1) and (e1 '), these are copied symmetrically to an axis of symmetry (yy) perpendicular to 01-C.
- the profiles (ice) and (e1's) are designed. These profiles engage with the weight piece W2, which has been copied symmetrically to the axis (yy).
- the tab L1 will engage with the pins W1 and W2.
- the weight piece W1 has the symmetry axis (w2) and the weight piece W2 has the symmetry axis (w2 ').
- the tab L1 is copied symmetrically to (w2) and to (w2 '). This results in the tabs L2 and L3.
- the thickness and width of the bars, the strength and shape of the tabs are determined by strength, acoustics, technology and other criteria.
- the geometry of the tabs can be chosen so that the tabs are shorter. This leads to better polygon effects and better acoustics.
- the pressure angle plays a major role in shaping and power transmission.
- the relative movement of the lug-weight piece can be regarded as a centroidal movement of the two centroids, pitch circle (w1) of the lug and pitch line (w2) of the rocker. Since these curves are virtual curves, the active profiles of the two parts, the involutes of the tab and the straight lines of the cogs will roll and slide. Despite the sliding movement, a high efficiency is achieved, similar to the involuntary procedures. Depending on the pressure angle, design of the tabs and cradles, the relative angle between two adjacent tabs may be larger or smaller.
- the chain can transmit a tensile force, wherein the axial force is transferred (in chain-pulling direction) from a tab to the cradle. Then the weight piece will be the next which in turn puts a load on the next weight piece.
- the amount of axial forces and frictional forces depends on the pressure angle and length of the tabs.
- Fig. 17 and Fig. 18 explain the structure of another embodiment of the joint.
- the rolling curves of the centroidal motion are the circle (w1) with the center 01 and the rolling line (w2), tangent at point C (FIG. 17).
- the engagement line (g) is tangent in A at the base circle (gl) and contains the instantaneous rotation C of the relative movement of the pitch circle (w1) and the rolling line (w2).
- a point K of the engagement line describes the involute (e1) during its rolling motion on the base circle.
- a generation straight line (gg) is considered vertically at point K.
- the generating line (gg) will describe the same involute (e1).
- the involute (e1) and the generation line (gg) are reciprocal enveloping curves.
- the two reciprocal enveloping curves are in contact at point K.
- the weighing piece W12 is designed so that it contains the generating line as an active profile.
- the involute (e1) and the active profile of the rocker are copied symmetrically to the axis 01-C. This results in the profiles (gg 1 ) and (e1 '). This gives an involute wheel-rack engagement.
- the pitch circle and the pitch line are the virtual centroids of the relative movement of the flap-piece.
- the tab L1 will contain the two involute profiles of the engagement and the cradle the two generation lines.
- the left profile of the tab, the curves (11) and (H ') are designed so that they do not collide with the adjacent load piece.
- the balance piece has two symmetry axes: (yy) perpendicular to 01 -C and 01 -C.
- the tab profiles (e1) and (e1 ') are copied symmetrically to the axis (yy).
- the profiles (e2) and (e2 ') are designed. These profiles are part of the tab L2 and with the wedge W12 in engagement.
- the weight piece W12 engages with the tabs L1 and L2.
- the weight piece W12 is copied symmetrically to the axis (w2) and forms the weight piece W23.
- the profiles of tab L2 (e2) and (e2 ') are copied symmetrically to the axis (w2). So the whole length of the tab is designed.
- the tab L1 is designed.
- the tab L1 is copied symmetrically from (w2) and forms the tab L3. It can be seen that the rocker W12 engage with the tabs L1 and L2 and the rocker W23 with the tabs L2 and L3. In this way, the next tabs and cradles of the chain are designed.
- the thickness and width of the bars, the strength and shape of the tabs are determined by strength, acoustics, technology and other criteria.
- the geometry of the tabs can be chosen so that the tabs become shorter (Fig. 18). This leads to an improvement of the Polygon effect and better acoustics.
- the pressure angle is important for shaping and power transmission.
- the relative movement of the lug-weight piece can be regarded as a centroidal movement of the two centroids, pitch circle (w1) of the lug and pitch line (w2) of the rocker. Since these curves are virtual curves, the active profiles of the two parts, the involutes of the tab and the lines of the cradles, will roll and slide. Despite the sliding movement, an efficiency similar to the involute procedures is achieved here as well. Depending on the pressure angle, design of the tabs and cradles, the relative angle between two adjacent tabs may be larger or smaller.
Abstract
Description
Claims
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE112006000670T DE112006000670A5 (de) | 2005-04-15 | 2006-03-24 | Laschenkette mit konvex-konkavem Kontakt der Wiegestücke |
JP2008505726A JP2008536068A (ja) | 2005-04-15 | 2006-03-24 | 揺動部材の凸面−凹面接触を備えたリンクプレートチェーン |
EP06722675A EP1891352A1 (de) | 2005-04-15 | 2006-03-24 | Laschenkette mit konvex-konkavem kontakt der wiegestücke |
US11/974,680 US20080096710A1 (en) | 2005-04-15 | 2007-10-15 | Plate-link chain with convex-concave contact of the rocker members |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102005017346.2 | 2005-04-15 | ||
DE102005017346 | 2005-04-15 |
Related Child Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US11/974,680 Continuation US20080096710A1 (en) | 2005-04-15 | 2007-10-15 | Plate-link chain with convex-concave contact of the rocker members |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2006108378A1 true WO2006108378A1 (de) | 2006-10-19 |
Family
ID=36617058
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/DE2006/000523 WO2006108378A1 (de) | 2005-04-15 | 2006-03-24 | Laschenkette mit konvex-konkavem kontakt der wiegestücke |
Country Status (5)
Country | Link |
---|---|
US (1) | US20080096710A1 (de) |
EP (1) | EP1891352A1 (de) |
JP (1) | JP2008536068A (de) |
DE (1) | DE112006000670A5 (de) |
WO (1) | WO2006108378A1 (de) |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP1754912A3 (de) * | 2005-08-18 | 2007-06-13 | Jtekt Corporation | Treibkette und Antriebsvorrichtung |
DE102012219773A1 (de) * | 2012-10-29 | 2014-04-30 | Schaeffler Technologies Gmbh & Co. Kg | Wiegegelenkkette |
DE102016204024A1 (de) * | 2016-03-11 | 2017-09-14 | Schaeffler Technologies AG & Co. KG | Laschenkette |
Families Citing this family (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102012024395A1 (de) * | 2012-12-13 | 2014-06-18 | Iwis Motorsysteme Gmbh & Co. Kg | Reibungsarme Hülsengelenkkette |
US10566301B2 (en) * | 2017-11-17 | 2020-02-18 | General Electric Company | Semiconductor logic device and system and method of embedded packaging of same |
US10396053B2 (en) | 2017-11-17 | 2019-08-27 | General Electric Company | Semiconductor logic device and system and method of embedded packaging of same |
US20230112146A1 (en) * | 2020-02-19 | 2023-04-13 | Schaeffler Technologies AG & Co. KG | Rocker pin for a rocker pin pair of a plate link chain |
Citations (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE3027834A1 (de) | 1980-07-23 | 1982-02-11 | P.I.V. Antrieb Werner Reimers GmbH & Co KG, 6380 Bad Homburg | Laschenkette fuer stufenlos verstellbare kegelscheibengetriebe |
DE3740504C1 (en) * | 1987-11-30 | 1989-06-15 | Walter Schopf | Flat link articulated chain for infinitely variably adjustable bevel crown gear mechanisms |
DE3826809C1 (de) | 1988-08-06 | 1989-08-24 | P.I.V. Antrieb Werner Reimers Gmbh & Co Kg, 6380 Bad Homburg, De | |
US4909778A (en) * | 1988-06-09 | 1990-03-20 | Reimers Getriebe Ag | Link chain for an infinitely variable cone disk or cone pulley transmission |
DE4429223C1 (de) * | 1994-08-18 | 1995-08-24 | Manfred Rattunde | Geräuscharme Laschenkette für Kegelscheibengetriebe |
EP0800018A1 (de) | 1996-04-03 | 1997-10-08 | CVT Verwaltungs GmbH & Co. Patentverwertungs KG | Laschenkette für stufenlos übersetzungseinstellbare Kegelscheibengetriebe |
DE10201979A1 (de) | 2001-02-06 | 2002-10-10 | Luk Lamellen & Kupplungsbau | Laschenkette für stufenlos verstellbare Kegelscheibengetriebe |
Family Cites Families (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE3129631C2 (de) * | 1981-07-28 | 1983-12-08 | P.I.V. Antrieb Werner Reimers GmbH & Co KG, 6380 Bad Homburg | Laschenkette für stufenlos verstellbare Kegelscheibengetriebe |
DE3413384C2 (de) * | 1984-04-10 | 1986-05-07 | P.I.V. Antrieb Werner Reimers GmbH & Co KG, 6380 Bad Homburg | Laschenkette für stufenlos verstellbare Kegelscheibengetriebe |
NL1000294C2 (nl) * | 1995-05-03 | 1996-11-05 | Gear Chain Ind Bv | Transmissieketting voor een kegeldrijfwerk. |
JP3420696B2 (ja) * | 1997-12-29 | 2003-06-30 | ボルグワーナー・モールステック・ジャパン株式会社 | サイレントチェーン伝動装置 |
JP3580415B2 (ja) * | 2000-04-05 | 2004-10-20 | 株式会社椿本チエイン | チェーン用ローラ及びローラを備えたチェーン |
-
2006
- 2006-03-24 DE DE112006000670T patent/DE112006000670A5/de not_active Withdrawn
- 2006-03-24 EP EP06722675A patent/EP1891352A1/de not_active Withdrawn
- 2006-03-24 WO PCT/DE2006/000523 patent/WO2006108378A1/de not_active Application Discontinuation
- 2006-03-24 JP JP2008505726A patent/JP2008536068A/ja active Pending
-
2007
- 2007-10-15 US US11/974,680 patent/US20080096710A1/en not_active Abandoned
Patent Citations (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE3027834A1 (de) | 1980-07-23 | 1982-02-11 | P.I.V. Antrieb Werner Reimers GmbH & Co KG, 6380 Bad Homburg | Laschenkette fuer stufenlos verstellbare kegelscheibengetriebe |
DE3740504C1 (en) * | 1987-11-30 | 1989-06-15 | Walter Schopf | Flat link articulated chain for infinitely variably adjustable bevel crown gear mechanisms |
US4909778A (en) * | 1988-06-09 | 1990-03-20 | Reimers Getriebe Ag | Link chain for an infinitely variable cone disk or cone pulley transmission |
DE3826809C1 (de) | 1988-08-06 | 1989-08-24 | P.I.V. Antrieb Werner Reimers Gmbh & Co Kg, 6380 Bad Homburg, De | |
DE4429223C1 (de) * | 1994-08-18 | 1995-08-24 | Manfred Rattunde | Geräuscharme Laschenkette für Kegelscheibengetriebe |
EP0800018A1 (de) | 1996-04-03 | 1997-10-08 | CVT Verwaltungs GmbH & Co. Patentverwertungs KG | Laschenkette für stufenlos übersetzungseinstellbare Kegelscheibengetriebe |
DE10201979A1 (de) | 2001-02-06 | 2002-10-10 | Luk Lamellen & Kupplungsbau | Laschenkette für stufenlos verstellbare Kegelscheibengetriebe |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP1754912A3 (de) * | 2005-08-18 | 2007-06-13 | Jtekt Corporation | Treibkette und Antriebsvorrichtung |
DE102012219773A1 (de) * | 2012-10-29 | 2014-04-30 | Schaeffler Technologies Gmbh & Co. Kg | Wiegegelenkkette |
DE102016204024A1 (de) * | 2016-03-11 | 2017-09-14 | Schaeffler Technologies AG & Co. KG | Laschenkette |
DE102016204024B4 (de) * | 2016-03-11 | 2018-02-01 | Schaeffler Technologies AG & Co. KG | Laschenkette |
Also Published As
Publication number | Publication date |
---|---|
JP2008536068A (ja) | 2008-09-04 |
DE112006000670A5 (de) | 2007-12-27 |
US20080096710A1 (en) | 2008-04-24 |
EP1891352A1 (de) | 2008-02-27 |
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