WO2005108819A1 - 動力伝達チェーン及びそれを用いた動力伝達装置 - Google Patents
動力伝達チェーン及びそれを用いた動力伝達装置 Download PDFInfo
- Publication number
- WO2005108819A1 WO2005108819A1 PCT/JP2005/008618 JP2005008618W WO2005108819A1 WO 2005108819 A1 WO2005108819 A1 WO 2005108819A1 JP 2005008618 W JP2005008618 W JP 2005008618W WO 2005108819 A1 WO2005108819 A1 WO 2005108819A1
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- WIPO (PCT)
- Prior art keywords
- chain
- pin
- power transmission
- hole
- link plates
- 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
- F16H—GEARING
- F16H9/00—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members
- F16H9/02—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members without members having orbital motion
- F16H9/04—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members without members having orbital motion using belts, V-belts, or ropes
- F16H9/12—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members without members having orbital motion using belts, V-belts, or ropes engaging a pulley built-up out of relatively axially-adjustable parts in which the belt engages the opposite flanges of the pulley directly without interposed belt-supporting members
- F16H9/125—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members without members having orbital motion using belts, V-belts, or ropes engaging a pulley built-up out of relatively axially-adjustable parts in which the belt engages the opposite flanges of the pulley directly without interposed belt-supporting members characterised by means for controlling the geometrical interrelationship of pulleys and the endless flexible member, e.g. belt alignment or position of the resulting axial pulley force in the plane perpendicular to the pulley axis
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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
- 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
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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
- F16H—GEARING
- F16H9/00—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members
- F16H9/02—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members without members having orbital motion
- F16H9/24—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members without members having orbital motion using chains or toothed belts, belts in the form of links; Chains or belts specially adapted to such gearing
Definitions
- the present invention relates to a power transmission chain used for a chain-type continuously variable transmission of a vehicle or the like, and a power transmission device using the same.
- a continuously variable transmission (CVT) of an automobile for example, a primary pulley provided on an engine side, a secondary pulley provided on a driving wheel side, and a plurality of link plates are provided. Some have a plurality of pins interconnecting these, and an endless power transmission chain bridged between both pulleys.
- a conical sheave surface of each pulley comes into contact with a part of a chain component such as a pin end surface of a power transmission chain, which occurs at this time. Traction is generated by frictional force to transmit power.
- the effective diameter of the pulley is continuously changed.
- the reduction ratio continuously changes, and a stepless speed change can be performed with a smooth motion different from the conventional gear type.
- a power transmission chain used in such a chain type continuously variable transmission is, for example, as described in Japanese Utility Model Laid-Open Publication No. 64-27558, in which a plurality of link plates are overlapped, and the Are connected by inserting a pin in a press-fit or loose-fit state.
- a force that enables a speed change between at least one of the primary pulley and the secondary pulley by continuously changing the groove width is generally such a chain.
- the pulley used in the continuously variable transmission has two sheave surfaces that are opposed to each other, and fixes one sheave surface in the pulley axial direction and moves the other sheave surface in the pulley axial direction.
- the width of the groove formed between the sheave surfaces can be changed.
- the center position of the groove width also moves because one sheave surface is fixed. This and In this case, the center of the groove width is shifted between the two pulleys, and misalignment occurs. Such misalignment is unavoidable to occur in the mechanism of this type of transmission!
- the power transmission chain as described above is formed so as to be able to bend (hereinafter also referred to as a circumferential bend) in a direction in which each pulley is wound around in a circumferential direction.
- Force Since the chain can hardly be moved in directions other than that direction, the chain is wound around both pulleys, and an excessive force is applied, and the contact surface between the sheave surface of the pulley and the chain can be properly maintained. Sometimes disappeared. If power transmission is performed for a long time in such a state, abnormal wear occurs on the sheave surface of the pulley and the contact surface on the chain side, and the power transmission efficiency decreases.
- the present invention has been made in view of such circumstances, and it is possible to appropriately allow misalignment between pulleys and effectively suppress occurrence of abnormal wear and reduction in power transmission efficiency. It is an object of the present invention to provide a transmission chain and a power transmission device using the same.
- the present invention includes, as chain components, at least a plurality of link plates having a through-hole, and a plurality of pin members penetrated through the through-hole and interconnecting the plurality of link plates. Used between a first pulley having a conical sheave surface and a second pulley having a conical sheave surface, wherein the chain member and the first and second pulleys are used.
- the power is transmitted by contact with the sheave surface, and the skew in the chain width direction per 200 mm of chain length is l to 2 mm.
- the skew amount indicating the degree of the flexibility in the width direction of the chain is set to an appropriate range, so that the first pulley and the Allows misalignment that is inevitable due to the mechanism that occurs between the second pulley Therefore, sufficient flexibility can be obtained, and the contact surfaces between the sheave surfaces of the two pulleys and the chain component can be appropriately maintained. Therefore, occurrence of abnormal wear and reduction in power transmission efficiency can be effectively suppressed.
- the skew amount When the skew amount is 1 mm or less, the above-described misalignment caused by the mechanism cannot be tolerated, and thus abnormal wear and a decrease in transmission efficiency may not be suppressed. If the skew amount is 2 mm or more, the flexibility of the power transmission chain is too large, the chain may flutter, and noise and vibration may increase. Further, the contact between the sheave surface and the power transmission chain becomes unstable, which may cause abnormal wear.
- the pin member may be inserted into the through-hole in a press-fit state. Even in this case, the occurrence of abnormal wear and a decrease in power transmission efficiency can be effectively suppressed.
- an end of an inner peripheral surface of the through hole is chamfered.
- the misalignment is allowed and the contact surfaces between the sheave surfaces of the two pulleys and the chain constituent members can be appropriately maintained, so that abnormal wear and a reduction in transmission efficiency can be effectively suppressed. Can be.
- the pin member forces the first pin passed through the through hole and the first pin through the through hole to contact one side surface of the pin! /
- the second pin has a side surface
- at least one of the side surface of the first pin and the one side surface of the second pin is provided with crowning in the chain width direction. Is preferred.
- the degree of freedom in the contact angle between the first pin and the second pin is generated by the crowning (convex curved surface) in the width direction of the chain, so that a chain having flexibility against bending other than circumferential bending can be obtained.
- the pin member is passed through the through hole.
- a second pin having one side surface that passes through the through-hole and is in contact with one side surface of the first pin, the inner peripheral surface of the through-hole of the link plate. It is preferable that gaps are provided between the other side of the first pin and at least one of between the inner peripheral surface of the through hole of the link plate and the other side of the second pin.
- the gap provides a degree of freedom in the angle formed between the longitudinal direction of the first pin or the second pin and the hole axis direction of the through-hole, so that it is flexible against bending other than circumferential bending. It can be made into a chain with character
- the power transmission chain includes the plurality of link plates arranged in the same phase in the longitudinal direction of the chain and overlapped in the width direction, and the pin member inserted into the plurality of link plates. And a plurality of pitch portions connected continuously in the longitudinal direction of the chain, at least one of the plurality of pitch portions is provided in a range near the center in the chain width direction. It is preferable that the plate is a centrally distributed pitch portion in which the plates are distributed unevenly.
- the link plates arranged closer to the left and right end portions that relatively strongly restrain the bending other than the circumferential bending are adjacent to each other as compared to the center portion closer to the center in the chain width direction. Coarse arrangement such that the interval between link plates is wide. For this reason, the restraining force of bending other than the circumferential bending of the central unevenly distributed pitch portion is reduced, and the bending becomes flexible with respect to the bending.
- the power transmission chain includes the plurality of link plates arranged in the same phase in the chain longitudinal direction and overlapped in the width direction, and the pin member inserted through the plurality of link plates.
- a plurality of pitch portions connected continuously in the longitudinal direction of the chain, at least one of the plurality of pitch portions is located closer to the center in the chain width direction and narrower than the entire width of the chain. It is preferable to be a central concentrated pitch section in which all the link plates constituting the pitch section are arranged.
- the central concentrated pitch portion has all the link plates constituting the central concentrated pitch portion arranged in a range narrower than the entire width of the chain. There is no link plate near the left or right end that restrains outside bending. For this reason, the central concentrated pitch portion has bending flexibility other than bending in the circumferential direction.
- the present invention also provides a first pulley having a conical sheave surface, a second pulley having a conical sheave surface, and a bridge between the first and second pulleys.
- the power transmission device configured as described above, even if misalignment inevitably occurring mechanically occurs between the first pulley and the second pulley, the power transmission described above is performed.
- the misalignment can be suitably tolerated by the flexibility of the transmission chain. Therefore, the contact surfaces between the sheave surfaces of the two pulleys and the chain component can be appropriately maintained, and abnormal wear and reduction in transmission efficiency can be effectively suppressed.
- FIG. 1 is a perspective view schematically showing a main configuration of a power transmission chain according to a first embodiment of the present invention.
- FIG. 2 is a circumferential sectional view of a part of the power transmission chain of FIG. 1.
- FIG. 3 is a top view showing an example of an arrangement of link plates in the power transmission chain of FIG. 1.
- FIG. 4 is a cross-sectional view of the chain taken along line BB in FIG. 2.
- FIG. 5 is a schematic view illustrating another shape of the inner peripheral surface end of the through hole of the link plate.
- FIG. 6 is a schematic diagram illustrating another shape of the inner peripheral surface end of the through hole of the link plate.
- FIG. 7 is a schematic view exemplifying another shape of the inner peripheral surface end of the through hole of the link plate.
- FIG. 8 is a top view for explaining a skew amount of the power transmission chain.
- FIG. 9 is a perspective view schematically showing a main configuration of a chain-type continuously variable transmission according to an embodiment of the power transmission device of the present invention.
- FIG. 10 is a side view for explaining a geometric relationship among a primary pulley, a secondary pulley, and a chain in the continuously variable transmission of FIG. 9.
- FIG. 11 is a cross-sectional view for explaining a geometric relationship among a primary pulley, a secondary pulley, and a chain in the continuously variable transmission shown in FIG.
- FIG. 12 is an axial sectional view of a pin and a strip when the chain according to the second embodiment of the power transmission chain of the present invention is viewed from above.
- FIG. 13 is a circumferential sectional view of a part of the power transmission chain according to a third embodiment of the present invention.
- FIG. 14 is a cross-sectional view in the chain width direction along line FF in FIG. 13.
- FIG. 15 is a top view showing an example of an array of link plates of a power transmission chain according to a fourth embodiment of the present invention.
- Fig. 16 is a diagram schematically illustrating an arrangement state of centrally unevenly distributed pitch portions with respect to the entire chain.
- FIG. 17 is a schematic view showing an example of a variation of the arrangement of link plates with respect to the entire chain width of one pitch portion.
- FIG. 18 is a schematic diagram showing another example of a variation of the arrangement of link plates with respect to the entire chain width of one pitch portion.
- FIG. 19 is a schematic diagram showing another example of a variation in the arrangement of link plates with respect to the entire chain width of one pitch portion.
- FIG. 20 is a schematic view showing another example of the variation of the arrangement of the link plates with respect to the entire width of the chain at one pitch portion.
- FIG. 21 is a top view showing an example of an array of link plates of a power transmission chain according to a fifth embodiment of the present invention.
- FIG. 22 is a view showing an example of a link plate in which a communicating portion for communicating the first through hole and the second through hole is formed.
- FIG. 23 In addition to a link plate having a communicating portion for communicating the first through-hole and the second through-hole. It is a figure showing the example of.
- FIG. 1 is a perspective view schematically showing a main part configuration of a so-called chain type continuously variable transmission chain (hereinafter, also simply referred to as “chain”) according to a first embodiment of the power transmission chain of the present invention.
- a chain 1 according to the present embodiment is endless, and has a plurality of link plates 20 that also have a metal (carbon steel or the like) force as a chain constituent member. It is composed of a plurality of pin members P which also have a metal (bearing steel or the like) force for connection. Note that, in FIG. 1, the description of the central portion in the width direction of the chain 1 is partially omitted.
- FIG. 2 is a cross-sectional view of a part of the chain 1 in the circumferential direction.
- the link plates 20 are formed such that the outline is a moderately curved shape and all have substantially the same outline.
- the link plate 20 is provided with one first through hole 21 and one second through hole 22 per sheet.
- the pin member P connecting the link plate 20 is formed as a first pin 30 which is a rod-shaped body having a predetermined cross section, and is formed to be slightly shorter than the pin 30 and
- the plurality of pins 30 and the plurality of strips 40 constituting the plurality of pin members P are all formed in substantially the same shape.
- the pin end surface 31 of the pin 30 has a convex curved surface set to a predetermined curvature, and contacts a sheave surface of a pulley of a chain type continuously variable transmission (not shown) to transmit power.
- FIG. 3 is an upper plan view showing an example of the arrangement of the link plates 20 in the chain 1.
- the plurality of link plates 20 are overlapped in the thickness direction and arranged in a predetermined order in the chain width direction and the chain longitudinal direction, and are connected in the first through hole 21 and the second through hole 22 to connect them.
- the pin member P is inserted through the hole.
- the plurality of pin members P are arranged substantially in parallel at a predetermined pitch determined by the distance between the first through-hole 21 and the second through-hole 22 formed in the link plate 20 in the longitudinal direction of the chain (see FIG. 2). ing.
- the pin member P is passed through the through holes 21 and 22 so that the plurality of link plates 20 can bend from each other as described later.
- the chain is positioned at the same position (the same phase) in the longitudinal direction of the chain.
- a predetermined number of link plates 20 arranged substantially parallel to the chain width direction and two sets of pin members P inserted therethrough constitute a pitch portion 60, and the chain 1 It is constituted by continuously connecting 60 in such a manner that it can be bent in the longitudinal direction of the chain.
- the first through-hole 21 is provided with a press fit for the pin 30 penetrated in the range indicated by the broken line J. That is, the pin 30 inserted into the first through-hole 21 is press-fitted into the first through-hole 21 in a range indicated by a broken line K.
- the strip 40 is inserted through the first through-hole 21 and the rolling strip 40 is passed through the first through-hole 21 to make rolling contact (or rolling contact including slight sliding contact) with the side surface of the pin 30. It is inserted so that it can rotate.
- the first through hole 21 is formed in a shape such that when the strip 40 rotates, the side surface of the strip 40 and the inner peripheral surface of the first through hole 21 can rotate while having a contact surface.
- the strip 40 penetrating through the second through hole 22 is press-fitted into the second through hole 22 with a range indicated by a broken line K.
- the pin 30 inserted into the second through-hole 22 can rotate while rolling (or rolling contact including a slight sliding contact) with the side surface of the strip 40 passed through the second through-hole. It has been inserted.
- the second through-hole 22 is formed in a shape such that when the pin 30 rotates, the side surface of the pin 30 and the inner peripheral surface of the second through-hole 22 can rotate while having a contact surface. .
- the pins 30 inserted through the first through-holes 21 in a press-fit state and the strips 40 inserted through the second through-holes 22 in a press-fit state can be fitted and pressed at room temperature.
- Cold-fitting The first through-hole 21 and the second through-hole 22 can be pressed by a method such as shrink fitting or cold fitting.
- the pin 30 rotatably penetrated through the second through hole 22 of the link plate 20 is adjacent to the link plate 20 and is displaced in the circumferential direction of the chain to be connected.
- 20a is press-fitted into the first through hole 21a of the link plate 20a.
- the strip 40 pressed into the second through hole 22 of the link plate 20 is rotatably passed through the first through hole 21a of the link plate 20a with respect to the link plate 20a.
- the pins 30 and the strips 40 press-fitted or passed through the link plates 20 and 20a rotate while rolling and in contact with each other, so that the link plates 20 and 20a can bend with each other.
- the chain 1 that can be bent in the circumferential direction is configured. T! / Puru.
- FIG. 4 is a cross-sectional view of the chain 1 taken along line BB in FIG.
- a chamfered portion 23 is provided at the inner peripheral end of the second through hole 22 of the link plate 20 over the entire periphery.
- a chamfer (not shown) is provided at the end of the inner peripheral surface of the first through hole 21.
- the chain 1 according to the present embodiment configured as described above has the chamfered portions at the inner peripheral end portions of the first and second through-holes 21 and 22, so that the longitudinal direction of the pin 30 and the Since there is a degree of freedom in the angle formed between the first and second through holes 21 and 22 and the hole axis direction, it has flexibility against bending in directions other than the circumferential bending.
- a chamfered portion 23 may be provided over substantially the entire surface, or, as shown in FIG. Further, as shown in FIG. 7, a crowning (convex curved surface) may be provided over substantially the entire surface including the ends of the inner peripheral surfaces of both through holes 21 and 22.
- the chamfering of the inner peripheral surfaces of the two through holes 21 and 22 can be performed by turning, but can also be provided by barrel polishing or the like.
- FIG. 8 is a top view of the chain for explaining the skew amount of the chain. Note that some illustrations of chain 1 are omitted in the figure.
- the chain 1 used in an endless state shows a state in which a part of the chain 1 is cut by a predetermined chain length L and aligned substantially straight without bending.
- the pin 30a located at one end 11 of the chain 1 is fixed so that it does not move in any direction.
- the present inventors set the width dimension due to this deviation to a chain length L.
- the skew amount in the width direction is defined as s. That is, the skew amount S indicates the degree of flexibility in the chain width direction.
- the chain 1 of the present embodiment has the flexibility in the width direction of the chain 1 by providing the chamfered portions on the inner peripheral surfaces 21 and 22 of the first and second through holes as described above. Is given.
- the shape of the chamfered portion 23 is set so that the skew S in the chain width direction per 200 mm of the chain length of the chain 1 is 1 to 2 mm.
- FIG. 9 is a perspective view schematically showing a main part configuration of a chain-type continuously variable transmission according to an embodiment of the power transmission device of the present invention including the above-described chain 1.
- This chain-type continuously variable transmission 50 (hereinafter, also simply referred to as “continuously variable transmission”) is mounted, for example, as a transmission of an automobile, and includes a metal primary pulley 51 as a first pulley and a second primary pulley 51.
- a secondary pulley 52 made of metal as the first pulley, and a chain 1 according to the present invention, which is bridged endlessly therebetween. Note that the cross section of the chain 1 in FIG. 9 is partially shown for easy understanding.
- the primary pulley 51 is integrally rotatably attached to an input shaft 53 connected to the engine side.
- the primary pulley 51 has a fixed sheave 51a having a conical sheave surface 51al, and faces the sheave surface 51al.
- a movable sheave 51b having a conical sheave surface 51bl arranged in a row.
- a groove is formed by the sheave surfaces 51al and 51bl of the sheave, and the groove holds the pin end surface 31 of the chain 1 from both sides in the width direction of the chain 1 with high pressure.
- a hydraulic actuator (not shown) is connected to the movable sheave 51b so that the movable sheave 51b can move in the axial direction of the input shaft 53.
- the movable sheave 51b When shifting, the movable sheave 51b is moved in the axial direction of the input shaft 53 to change the groove width of the groove formed by the sheave surfaces 51al and 51bl. Since the chain width of the chain 1 is always constant, the chain 1 is wound around the primary pulley 51 at a radial position commensurate with the chain width, and the winding radius of the chain 1 around the input shaft 53 can be changed. RU
- the secondary pulley 52 is rotatably attached to an output shaft 54 connected to the driving wheel side, and like the primary pulley 51, a sheave for forming a groove for sandwiching the chain 1 under high pressure.
- a fixed sheave 52a having a surface and a movable sheave 52b are provided.
- a groove is formed by the sheave surfaces 52al and 52bl of these sheaves, and the groove holds the pin end surface 31 of the chain 1 with both sides in the chain width direction being strongly pressed.
- a hydraulic actuator (not shown) is connected to the movable sheave 52b, whereby the movable sheave 52b is movable in the axial direction of the output shaft 54.
- the movable sheave 52b When shifting, the movable sheave 52b is moved in the axial direction of the output shaft 54 to change the groove width of the groove formed by the sheave surfaces 52al and 52b1. Since the chain width of the chain 1 is always constant, the chain 1 is wound around the secondary pulley 52 at a radial position corresponding to the chain width so that the winding radius of the chain 1 around the output shaft 54 can be changed. Become.
- the continuously variable transmission 50 can be performed as follows.
- the groove width on the primary pulley 51 side is enlarged by moving the movable sheave 51b to reduce the winding radius of the chain 1 on the primary pulley 51.
- the groove width on the secondary pulley 52 side is reduced by moving the movable sheave 52b to increase the winding radius of the chain 1 on the secondary pulley 52.
- the groove width on the primary pulley 51 side is reduced by moving the movable sheave 51b to thereby reduce the primary pulley 51 of the chain 1.
- the groove width on the secondary pulley 52 side is enlarged by the movement of the movable sheave 52b to reduce the winding radius on the secondary pulley 52 of the chain 1. In this way, by changing the winding radius of the chain 1 around the input shaft 53 and the output shaft 54, the speed between the input shaft 53 and the output shaft 54 can be increased or decreased.
- FIG. 10 is a side view for explaining the geometric relationship between the primary pulley 51, the secondary pulley 52, and the chain 1 wound therearound in the continuously variable transmission 50.
- the figure shows a state where the speed ratio is set to n, for example.
- the effective radius of the primary pulley 51 is Rp and the effective radius of the secondary pulley 52 is Rs, these relations are expressed by the following equation (1).
- a broken line 58 shows the relationship between the primary pulley 51, the secondary pulley 52, and the chain 1 when the gear ratio n is 1, and the effective radii Rp and Rs of both pulleys in this case are the same. Become.
- the effective radius Rc of both pulleys at this time is expressed by the following equation (4) from the above equations (1) and (3).
- FIG. 11 is a cross-sectional view on a straight line 57 for explaining the geometric relationship between the primary pulley 51, the secondary pulley 52, and the chain 1 in FIG. It should be noted that input / output axes and the like are omitted for ease of understanding.
- the effective radius Rp of the primary pulley 51 is smaller than Rc as shown in FIG. 10, so that the movable sheave 51b has a larger width of the pulley groove 61 formed by the sheave surfaces 51al and 51bl. Then, it moves in the direction away from the fixed sheave 51a. Chain 1 is located at a distance of Rp from the center line 55a of the primary pulley 51. At this time, the groove width center line 61a of the pulley groove 61 moves toward the movable sheave 5 lb along with the movement of the movable sheave 51b.
- the broken line 62a indicates the movable sheave 51b when the effective radius Rp is Rc
- the broken line 62b indicates the position of the chain 1 at this time
- the broken line 64a indicates the movable sheave 52b when the effective radius Rs is Rc.
- a broken line 64b indicates the position of the chain 1 at this time.
- the effective radius of both pulleys 51 and 52 is Rc
- the two pulleys 51 and 52 are configured such that their groove width centers coincide with each other.
- the groove width centers of both pulleys 51 and 52 are indicated by a straight line U!
- the movement amount of the groove width center line 61a is considered with reference to the straight line U. That is, the movement amount Hp, which is the displacement between the groove width center line 61a and the straight line U, is expressed by the following equation (5), where ⁇ is the inclination angle of the sheave surfaces 51al and 51bl.
- the movable sheave 52b has a large pulley groove 63 formed by the sheave surfaces 52al and 52bl. It moves in the direction approaching the fixed sheave 52a so that it becomes closer.
- the chain 1 is located at a distance of Rs from the center line 56a of the secondary pulley 52. At this time, the groove width center line 63a of the pulley groove 63 moves toward the fixed sheave 52a along with the movement of the movable sheave 52b.
- the movement amount of the groove width center line 63a is also considered based on the straight line U as in the case of the primary pulley 51 described above. That is, the movement amount Hp, which is the displacement between the groove width center line 63a and the straight line U, is expressed by the following equation (6), where ⁇ is the inclination angle of the sheave surfaces 52al and 52bl.
- the primary pulley 51 has a movable sheave 51b disposed below the paper with respect to the straight line U
- the secondary pulley 52 has a movable sheave 52b disposed above the paper with respect to the straight U. ing.
- the shaft dimension Is is fixed, if the groove width of one pulley is widened, the groove width of the other pulley is always narrow, the groove width center of both pulleys must be in the same direction with respect to the straight line U. Will move to.
- misalignment due to the difference between the movement amounts Hp and Hs, a deviation from the center of the groove width between the primary pulley 51 and the secondary pulley 52, that is, misalignment occurs. Such a misalignment is unavoidable in the mechanism of the continuously variable transmission 50 in which the speed is changed by changing the groove width of the pulley as described above.
- the misalignment amount M at this time is expressed by the following equation (7).
- the chain 1 according to the present embodiment used in the above-described continuously variable transmission 50 has the chamfered portion 23 at the end of the inner peripheral surface of the first and second through holes 21 and 22 of the link plate 20.
- the flexibility in the chain width direction is provided so that the skew amount S in the chain width direction per 200 mm of the chain length is l to 2 mm.
- the skew amount S is 1 mm or less, misalignment that occurs in the mechanism described above cannot be tolerated, and therefore, abnormal wear and a decrease in transmission efficiency may not be suppressed. If the skew S is 2 mm or more, the deformability of the chain 1 is too large, and the chain 1 may flutter, resulting in increased noise and vibration. In addition, contact between each sheave and the pin end surface 31 of the chain 1 becomes unstable, which may cause abnormal wear.
- the chain 1 of the present embodiment is provided with sufficient flexibility necessary to allow misalignment inevitably occurring in the mechanism as described above.
- the contact surface between the sheave surface and the pin end surface 31 can be appropriately maintained. Therefore, even when the power transmission is performed for a long period of time by being incorporated in the continuously variable transmission 50, abnormal wear and reduction in transmission efficiency can be effectively suppressed.
- the continuously variable transmission 50 even if a misalignment inevitably occurring mechanically between the two pulleys 51 and 52 occurs, the chain Since line 1 is provided with flexibility with an appropriate amount of skew, the misalignment can be appropriately tolerated, and the contact surface between the sheave surfaces of both pulleys 51 and 52 and the pin end surface 31 can be appropriately maintained. it can. Therefore, even if power is transmitted for a long period of time, abnormal wear and abnormal Can be effectively suppressed. For this reason, it is a continuously variable transmission that can stably transmit power for a long time.
- FIG. 12 is an axial sectional view of pins and strips when the chain according to the second embodiment of the power transmission chain of the present invention is viewed from above.
- the main difference between the present embodiment and the first embodiment is that the first and second through holes 21 and 22 of the link plate 20 are provided with chamfers at the inner peripheral end portions thereof.
- the point that the side of the contact portion T side of the pin 30 that contacts the strip 40 at the contact portion T is provided with a crown 1 (convex curved surface) in the width direction of the chain 1.
- the curvature of Klaujung is exaggerated in order to make the shape easier to grasp.
- the other points are the same as in the first embodiment, and the description is omitted.
- the crowning in the width direction of the chain is provided on one side surface of the pin 30, a gap d is formed between the pin 30 and both ends of the strip 40 in the circumferential direction of the chain.
- the gap d has the maximum value dm at both ends of the strip 40.
- the maximum value dm of the gap d depends on the applied curvature.
- the longitudinal length of the strip 40 is shorter than that of the pin 30, so that the gap d is maximum at both end positions of the strip 40.
- the gap d means a gap generated by the crown jung provided in the width direction of the chain, and the gap Q existing between the pin 30 and the strip 40 without a strong crowd jung (see FIG. 2). Not the gap distance.
- the degree of freedom in the contact angle between the pin 30 and the strip 40 is generated by crowning (convex curved surface) in the width direction of the chain provided on one side surface of the pin 30. It has flexibility against bending in directions other than bending. For this flexibility, the maximum value dm of the gap d was set so that the skew amount S force in the chain width direction per chain length of 200 mm of the chain 1 was ⁇ 2 mm.
- the method of measuring the maximum value dm of the gap d is determined as follows.
- the maximum value dm of the gap d is related to the flexibility of the chain 1, the maximum value dm is within a range in which the contact portion T can move by bending the chain 1 (in any direction). It does not take into account the gap distance of the part that is the largest value in the chain 1 that is not likely to be related to the flexibility of the chain 1. That is, for example, in FIG. 12, there is a recess on one side of the opposing pin 30 or strip 40, or the gap d is extremely increased near both ends of the pin 30 or strip 40, and the chain 1 is If there is a part that cannot be the contact part T even if it is bent to the limit in any direction, the gap distance of the part is not considered.
- the chain 1 according to the present embodiment having the above-described configuration is configured such that the chain 1 is provided on one side surface of the pin 30 in the width direction of the chain (convex curved surface) to enter the continuously variable transmission 50 for a long time. Even if power is transmitted for a long time, abnormal wear and reduction in transmission efficiency can be effectively suppressed. Further, in the present embodiment, since the contact angle between the pin 30 and the strip 40 can be made relatively large, it is easy to obtain higher flexibility at both ends as compared with the first embodiment. In addition, by adjusting the maximum value dm of the gap d, it becomes easy to set the flexibility required for the chain 1. In the present embodiment, the contact portion T side of the force strip 40 in which the pin 30 is provided with the crowning is provided. It is permissible to provide a crowded wing on the side of the car, or to provide a crowded wing on both sides.
- FIG. 13 is a circumferential sectional view of a part of a power transmission chain according to a third embodiment of the present invention.
- the main difference between the present embodiment and the first embodiment is that no chamfer is provided at the inner peripheral end of the first and second through holes 21, 22 of the link plate 20, and The point is that gaps el and e2 are provided between the side surfaces of the pins 30 that are not in contact with the strip 40 and the inner peripheral surfaces of the first and second through holes 21 and 22.
- the other points are the same as those of the first embodiment, and the description is omitted.
- the chain 1 of the present embodiment allows the first and second directions of the pin 30 to be aligned with the gap el and e2. Since there is a degree of freedom in the angle formed between the first through hole 21 and the second through hole 21 and the hole axis direction, the second through hole 21 and the second through hole 21 have flexibility with respect to bending in directions other than the circumferential bending. For this flexibility, the gaps el and e2 are set so that the skew amount S in the chain width direction per chain length 200 mm of the chain 1 is 1 to 2 mm. Note that the gap e2 does not indicate a gap required for the pin 30 to rotate in the second through-hole 22, but indicates a gap for imparting freedom to the longitudinal angle of the pin 30.
- FIG. 14 is a cross-sectional view in the chain width direction along line FF in FIG.
- the gap 30 is provided between the side surface of the pin 30 and the inner peripheral surface of the first through hole 21 as described above, the pin 30 is not pressed into the first through hole 21 (the second through hole 21). 22 was not originally press-fitted). Therefore, projections 33 are formed on the side surfaces 32 on both ends of the pin 30, and the projections 33 lock the link plate 20 so that the link plate 20 does not fall off.
- the protrusion 33 may have any shape as long as the link plate 20 can be locked.
- the protrusion may be formed along the outer circumference of both ends of the pin 30 or may be formed only on the side surface of the first through hole 21 facing the inner wall surface.
- the projection may be divided into a plurality of portions. Such a projection can be easily formed using a caulking tool or the like. Further, the projection 33 may be formed by fixing another member such as a ring-shaped member (retaining ring, snap ring), a split pin, a clip, a retainer, or the like to the pin or the strip.
- a ring-shaped member retaining ring, snap ring
- a split pin split pin
- a clip a retainer, or the like
- the chain 1 according to the present embodiment configured as described above has gaps el and e2, so that even if the chain 1 is incorporated in the continuously variable transmission 50 and power is transmitted for a long period of time, abnormal wear and reduction in transmission efficiency are caused. Can be effectively suppressed. Further, in the present embodiment, if the shapes of the first and second through holes 21 and 22 are changed, the flexibility of the chain 1 can be obtained, so that the above-mentioned effect can be easily obtained.
- the projections 33 are provided on both side surfaces of the pins 30 to lock the link plate 20, so that it is possible to effectively prevent a problem that the link plate 20 falls off. it can.
- gaps el and e2 are provided between the side surface of the pin 30 and the inner peripheral surfaces of the first and second through holes 21 and 22 of the link plate 20.
- Shape protrusion 33 Although the configuration is described, the present invention is not limited to this. That is, between the inner peripheral surface of the first and second through holes 21 and 22 and the side surface of the pin 30 and between the inner peripheral surface of the first and second through holes 21 and 22 and the side surface of the strip 40. It is sufficient that at least one has a gap that allows misalignment. Also, projections for locking the link plate 20 should be formed on the side surfaces of at least one of both ends of the pin 30 and the strip 40 for preventing the link plate 20 from dropping off.
- FIG. 15 is a top view showing an example of the arrangement of the link plate of the power transmission chain according to the fourth embodiment of the present invention.
- the main difference between the present embodiment and the first embodiment is that a chamfered portion is provided at the inner peripheral end of the first and second through holes 21 and 22 of the link plate 20, so that the And that the chain 1 is configured such that the center unevenly distributed pitch portion 62 in which the link plate 20 is unevenly distributed in a range near the center in the chain width direction is arranged in a part of the plurality of pitch portions.
- the other points are the same as in the first embodiment, and a description thereof will be omitted.
- the center unevenly distributed pitch portions 62 are arranged between two adjacent (two sets) of pin members P1 and between the two sets of pin members P1 near the center in the chain width direction. It comprises a link plate 201 and four link plates 202 arranged closer to the end in the chain width direction than this.
- the link plates 201, 202, and 203 in FIG. 15 are given different reference numerals to explain the arrangement of the link plates 20 below the force having substantially the same shape as the link plate 20 described above.
- the pin member P1 has substantially the same shape as the above-described pin member P, but is denoted by another reference numeral for describing the pin member P constituting the center unevenly distributed pitch portion 62.
- the link plates of the central unevenly distributed pitch portion 62 are arranged as follows.
- the five link plates 201 are arranged near the center in the chain width direction with almost no gap, and the remaining four link plates 202 are arranged two by two on the left and right near the end in the chain 1 width direction. ing.
- the link plates 202 which are arranged adjacent to the left and right of the five link plates 201 arranged in an overlapping manner are arranged so as to overlap with the pitch portions 63 which are adjacently connected to both sides in the chain circumferential direction of the central uneven pitch portion 62.
- the link plates 20 are arranged on the left and right with an interval of approximately three thicknesses of the link plates 20 sandwiching the three link plates 203.
- the link plates 202 arranged on the chain width direction end side of the link plates 202 arranged at intervals are arranged so as to sandwich one link plate 20 arranged in the pitch portion 63.
- the link plates 20 are arranged on the left and right ends in the width direction of the chain at intervals of about one sheet of the thickness of the link plates 20.
- the arrangement of the link plates 202 is a coarse arrangement such that the interval between the adjacent link plates is wider than the arrangement of the five link plates 201.
- the pitch portion 63 connected adjacent to both sides of the central uneven pitch portion 62 in the circumferential direction of the chain and the pitch portion 64 connected to the other portion that is not connected to the central uneven pitch portion 62 of the pitch portion 63 are connected to the link plate 20 in the chain width direction.
- the link plates 20 are arranged so that the pitch portions 61 arranged at equal intervals can be connected.
- FIG. 16 is a diagram schematically illustrating an arrangement state of the center unevenly distributed pitch portion 62 with respect to the entire chain 1.
- individual pitch portions are represented in a rectangular parallelepiped shape, and a state in which they are connected to form the chain 1 is shown.
- the hatched portion in the figure is the center uneven pitch portion 62
- the unhatched portion is the center uneven pitch portion such as a pitch portion in which the link plates 20 are arranged at equal intervals in the chain width direction.
- 62 a fixed number of pitch portions are connected.
- the chain 1 according to the present embodiment is configured such that the center unevenly distributed pitch portions 62 are always connected at regular intervals in the chain circumferential direction.
- the center unevenly distributed pitch portion 62 relatively strongly restrains the bends other than the circumferential bend of the pitch portion, and the link plates arranged near the left and right end portions. 20 has a coarse arrangement in which the distance between adjacent link plates 20 is wider than that near the center in the chain width direction. Therefore, the binding force of the pitch portion other than the bending in the circumferential direction is reduced, and the pitch portion has flexibility with respect to the bending. Since the central uneven pitch portions 62 provided with such flexibility are arranged at regular intervals in the circumferential direction of the chain, the entire chain 1 can be provided with flexibility. In this flexibility, the center unevenly distributed pitch portion 62 is arranged so that the skew S in the chain width direction per 200 mm of the chain length of the chain 1 is l to 2 mm.
- the chain 1 according to the present embodiment configured as described above has the center unevenly distributed pitch portions 62 appropriately arranged as described above, and is incorporated in the continuously variable transmission 50 to transmit power for a long time.
- abnormal wear and reduction in transmission efficiency can be effectively suppressed.
- the flexibility of the entire chain 1 can be imparted only by changing the arrangement of the link plates 20 in the pitch portion, so that the shapes of the pins 30, the strips 40, the first and second through holes 21, 22 and the like are changed. It can be implemented without change from the conventional one.
- 17 to 20 are schematic diagrams showing variations of the arrangement of the link plates 20 with respect to the entire chain width of one pitch portion.
- the link plates 20 are all arranged at equal intervals.
- FIG. 18 three sheets are arranged in the center with almost no gap therebetween, and the other link plates 20 are arranged on the left and right at equal intervals of about one thickness of the link plate 20. .
- FIG. 19 four sheets are arranged in the center with almost no gap, and the other link plates 20 are arranged on the left and right at equal intervals of about one sheet thickness of the link plate 20.
- two sets of link plates 20 are arranged at the center of the link plate 20 so as to be overlapped with almost no gap, and are arranged at intervals of about one sheet of the thickness of the link plate 20.
- the link plates 20, which are arranged adjacent to the end portions in the chain width direction of the link plates 20, which are arranged one above the other with almost no gap, are spaced at intervals of about one thickness of the link plates 20. They are arranged on the left and right.
- the link plates 20 arranged on the end side in the chain width direction of the link plates 20 arranged at an interval of about one sheet of the thickness of the link plate 20 are equivalent to about three sheets of the thickness of the link plate 20. They are arranged on the left and right sides in the chain width direction with an interval.
- the center unevenly distributed pitch portion is such that link plates 20 are arranged near both ends of the entire chain at least one at each end, and are located near the center in the chain width direction.
- the center unevenly distributed pitch portion is not limited to the examples shown in FIGS.
- FIG. 21 is a top view showing an example of an array of chain link plates according to a fifth embodiment of the power transmission chain of the present invention.
- the main difference between the present embodiment and the fourth embodiment is that, instead of the central uneven pitch portion, the entire width of the chain is closer to the center in the chain width direction.
- the point is that a central concentrated pitch section 65 in which all the link plates 20 constituting the pitch section are arranged in a range narrower than G.
- the other points are the same as in the fourth embodiment, and the description is omitted.
- the chain 1 according to the present embodiment is configured such that the central concentrated pitch portions 65 are always connected at regular intervals in the circumferential direction of the chain, similarly to the fourth embodiment. .
- This central concentrated pitch portion 65 is different from the central uneven pitch portion in that the link plates 20 are not arranged near both ends of the entire chain width G.
- the entire chain width G refers to the width dimension of the pitch portion that is the widest in the chain width direction and is arranged in the chain width in chain 1 in FIG.
- the central concentrated pitch portion 65 is composed of two sets of pin members P2 and nine link plates 204, and all nine link plates 204 arranged between the two sets of pin members P2 Are arranged near the center in the width direction of the chain 1 with almost no gap.
- the pitch portion 66 connected adjacent to both ends of the central concentrated pitch portion 65 in the chain circumferential direction is composed of ten link plates 205, and the link plates are located near the left and right ends in the chain width direction. 205 are superimposed on each other with substantially no gap, and the nine link plates 204 constituting the central concentrated pitch portion 65 are arranged so as to sandwich both side forces.
- a pitch portion 67 in which nine link plates 20 are arranged is connected, and the link plates 20 are arranged at equal intervals in the chain width direction.
- the link plates 20 are arranged so that the pitch portions 61 can be connected.
- the central concentrated pitch portion 65 restricts bending other than bending in the circumferential direction, and there is no link plate near the left and right ends. Flexibility against bending other than bending is suitably obtained, and flexibility can be imparted to the entire chain 1. In this flexibility, the central concentration pitch section 65 is arranged so that the skew S in the chain width direction per 200 mm of the chain length of the chain 1 is 1 to 2 mm.
- the chain 1 according to the present embodiment having the above-described configuration is configured such that the centrally-concentrated pitch portion 65 is appropriately disposed as described above. In addition, abnormal wear and reduction in transmission efficiency can be effectively suppressed. Further, in the fourth embodiment, the link plate 20 is disposed near the end of the central uneven pitch portion 62 in the chain width direction. However, since the link plates 20 are not arranged near the ends in the chain width direction in the central concentrated pitch portion 65 of the present embodiment, higher flexibility can be obtained. As a result, the degree of freedom in designing the chain 1 is increased, such as the number and positions of the central concentrated pitch portions 65 with respect to the entire chain 1.
- the link plate 20 of the power transmission chain 1 shown in each of the above embodiments has a force formed with two through holes (first and second through holes 21 and 22) as shown in FIG.
- a communication portion 25 may be formed to allow the two through holes 21 and 22 to communicate with each other.
- a communication portion 25 is provided so as to cross the pillar portion 26 between the through holes 21 and 22 in the longitudinal direction of the link plate.
- the deformation of the link plate 2 becomes easy, and when a large force is received from the pin 3 or the strip 4, the stress concentration at the peripheral portion of the through hole can be reduced. Durability is improved. In a press-fit chain in which pins and strips are fitted and fixed to the link plate, the effect of improving the durability by relieving the stress concentration is particularly great.
- the width of the communication portion 25 shown in FIG. 22 is relatively narrow, and in the modified example shown in FIG. 23, the width of the communication portion 25 is relatively wide.
- the width of the communication portion 25 is reduced, the rigidity of the link plate is increased as compared with the case where the width is wide, and deformation of the link plate when the link plate is manufactured by punching can be suppressed.
- the width of the communication portion 25 is increased, the deformation of the link plate is further facilitated as compared with the case where the width is narrow, so that the effect of alleviating stress concentration is increased.
- the width of the communication portion 25 may be appropriately determined according to the link size, the load condition, and the like.
- a power transmission chain includes, for example, a power transmission chain configured to provide a contact portion with a sheave surface on a link plate to perform power transmission, and a power transmission chain other than a component of the chain according to the present embodiment.
- the present invention can also be applied to a power transmission chain or the like configured to provide a contact member (such as a friction block) on a chain and thereby transmit power.
- the pin 30 as the first pin and the strip 40 as the second pin are formed by bending the force link plate having different cross-sectional shapes. As long as it can be connected, the pin 30 (first pin) and the strip 40 (second pin) having the same cross-sectional shape can be used.
- the chain 1 bridged between the primary pulley 51 and the secondary pulley 52 includes the above-described second to fifth chains. It goes without saying that the chain according to the embodiment (see FIGS. 12 to 23) may be used.
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Transmissions By Endless Flexible Members (AREA)
Abstract
Description
Claims
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US11/579,876 US20080254927A1 (en) | 2004-05-11 | 2005-05-11 | Power Transmission Chain and Power Transmission Device Using the Same |
EP05739326A EP1760361A4 (en) | 2004-05-11 | 2005-05-11 | POWER TRANSMISSION CHAIN AND POWER TRANSMITTING DEVICE USING THE SAME |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2004140877A JP2005321066A (ja) | 2004-05-11 | 2004-05-11 | 動力伝達チェーン及びそれを用いた動力伝達装置 |
JP2004-140877 | 2004-05-11 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2005108819A1 true WO2005108819A1 (ja) | 2005-11-17 |
Family
ID=35320295
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2005/008618 WO2005108819A1 (ja) | 2004-05-11 | 2005-05-11 | 動力伝達チェーン及びそれを用いた動力伝達装置 |
Country Status (6)
Country | Link |
---|---|
US (1) | US20080254927A1 (ja) |
EP (1) | EP1760361A4 (ja) |
JP (1) | JP2005321066A (ja) |
KR (1) | KR20070020291A (ja) |
CN (1) | CN100441905C (ja) |
WO (1) | WO2005108819A1 (ja) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2008077365A1 (de) * | 2006-12-22 | 2008-07-03 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Laschenkette |
EP1840408A3 (en) * | 2006-03-30 | 2010-10-06 | JTEKT Corporation | Power transmission chain, and power transmission system having the same |
Families Citing this family (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
KR20080077999A (ko) * | 2005-12-21 | 2008-08-26 | 루크 라멜렌 운트 쿠프룽스바우 베타일리궁스 카게 | 요람형 압력 부재의 제조 방법 및 엠보싱 장치 |
JP2009174606A (ja) * | 2008-01-23 | 2009-08-06 | Tsubakimoto Chain Co | サイレントチェーン |
NL1039424C2 (nl) * | 2012-02-29 | 2013-09-02 | Gear Chain Ind Bv | Borging pennen. |
WO2015124151A1 (de) * | 2014-02-24 | 2015-08-27 | Schaeffler Technologies AG & Co. KG | Laschenkette |
KR102208808B1 (ko) | 2014-03-28 | 2021-01-28 | 삼성전자주식회사 | 링크 조립체, 프레임 및 이를 포함하는 보행보조로봇 |
CN105833586A (zh) * | 2016-05-06 | 2016-08-10 | 新疆惠利灌溉科技股份有限公司 | 悬浮式过滤器 |
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JP2005054940A (ja) * | 2003-08-06 | 2005-03-03 | Koyo Seiko Co Ltd | 動力伝達チェーン及びそれを用いた動力伝達装置 |
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JP2005214345A (ja) * | 2004-01-30 | 2005-08-11 | Koyo Seiko Co Ltd | 動力伝達チェーンおよびその製造方法ならびに動力伝達装置 |
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JPS6130739U (ja) * | 1984-07-28 | 1986-02-24 | 本田技研工業株式会社 | チエ−ン式vベルト |
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- 2005-05-11 EP EP05739326A patent/EP1760361A4/en not_active Withdrawn
- 2005-05-11 US US11/579,876 patent/US20080254927A1/en not_active Abandoned
- 2005-05-11 KR KR1020067026081A patent/KR20070020291A/ko not_active Application Discontinuation
- 2005-05-11 CN CNB2005800150703A patent/CN100441905C/zh not_active Expired - Fee Related
- 2005-05-11 WO PCT/JP2005/008618 patent/WO2005108819A1/ja active Application Filing
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Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP1840408A3 (en) * | 2006-03-30 | 2010-10-06 | JTEKT Corporation | Power transmission chain, and power transmission system having the same |
US8038561B2 (en) | 2006-03-30 | 2011-10-18 | Jtekt Corporation | Power transmission chain, and power transmission system having the same |
WO2008077365A1 (de) * | 2006-12-22 | 2008-07-03 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Laschenkette |
US9261166B2 (en) | 2006-12-22 | 2016-02-16 | Schaeffler Technologies AG & Co. KG | Plate-link chain |
Also Published As
Publication number | Publication date |
---|---|
CN100441905C (zh) | 2008-12-10 |
EP1760361A4 (en) | 2010-01-06 |
US20080254927A1 (en) | 2008-10-16 |
JP2005321066A (ja) | 2005-11-17 |
EP1760361A1 (en) | 2007-03-07 |
KR20070020291A (ko) | 2007-02-20 |
CN1954160A (zh) | 2007-04-25 |
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