WO2015008692A1 - 無段変速機用ベルト - Google Patents
無段変速機用ベルト Download PDFInfo
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- WO2015008692A1 WO2015008692A1 PCT/JP2014/068425 JP2014068425W WO2015008692A1 WO 2015008692 A1 WO2015008692 A1 WO 2015008692A1 JP 2014068425 W JP2014068425 W JP 2014068425W WO 2015008692 A1 WO2015008692 A1 WO 2015008692A1
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- layer
- metal
- friction coefficient
- metal ring
- belt
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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
Definitions
- the present invention relates to a continuously variable transmission belt in which a plurality of metal elements are supported on a metal ring assembly in which a plurality of metal rings are stacked in order to transmit a driving force between a drive pulley and a driven pulley.
- DLC Diamond-like Carbon: Diamond-like Carbon having a granular protrusion shape on a metal member having a predetermined surface roughness
- a high speed sliding member coated with a membrane is described.
- Patent Document 2 as a continuously variable transmission belt for improving the durability of a metal ring, there is a continuously variable transmission belt in which a mountain-like protruding portion is formed on the inner circumferential surface of the innermost circumferential metal ring. Have been described.
- the average contact width of the projections measured in the direction perpendicular to the traveling direction should be a predetermined size. Can prevent the occurrence of cracks.
- Patent No. 4918972 gazette Patent No. 4078126
- the present invention has been made in view of the above-described points, and an object thereof is to provide a continuously variable transmission belt capable of achieving both reduction in friction resistance of a metal ring and improvement in durability. is there.
- a belt for a continuously variable transmission is a metal in which a plurality of metal rings (33) are laminated in order to transmit a driving force between a driving pulley (6) and a driven pulley (11).
- a continuously variable transmission belt supporting a plurality of metal elements (32) on a ring assembly (31), the plurality of protrusions (38a) formed on the surface (33a) of the metal ring (33) And a plurality of valleys (38b) formed between the plurality of protrusions (38a) and the uneven surface (38) having a plurality of valleys (38b), and the valleys (38b) in the uneven surface (38) It is characterized in that a low friction coefficient layer (51) having a coefficient lower than that of the surface of the projection (38a) is formed. Further, in this continuously variable transmission belt, the uneven surface (38) has a structure in which a plurality of mountain-like projections (38a) extending in a diagonal direction with respect to the traveling direction of the metal ring (33) It may be.
- the friction coefficient of the surface of the metal ring can be suppressed low by the low friction coefficient layer formed in the valley portion of the uneven surface of the metal ring.
- the frictional resistance due to the sliding between the metal ring and the metal element can be reduced.
- the average contact width in the left-right direction (width direction) of the protrusions after initial wear is By setting in such a manner, it is possible to prevent the depthwise development of the pitching that has occurred on the top of the projection when the projection is initially worn.
- the uneven surface (38) is at least the innermost metal ring (33) of the plurality of metal rings (33) constituting the metal ring assembly (31). It is good to form in a surrounding surface (33a).
- the frictional resistance generated at the contact point between the metal ring and the inner peripheral surface of the metal ring at the innermost periphery is the largest as the frictional resistance due to differential rotation between members generated internally.
- the uneven surface is formed on the inner circumferential surface of the innermost metal ring, and the low friction coefficient layer is formed on the valley portion of the uneven surface.
- the coefficient of friction of the inner circumferential surface of can be kept low. As a result, the frictional resistance generated between the metal ring assembly and the metal element can be reduced, so that the power transmission efficiency (belt efficiency) of the continuously variable transmission belt can be improved. Therefore, it is possible to provide a high-strength, high-efficiency continuously variable transmission belt.
- a nitrided layer (52) be formed as an underlayer of the low friction coefficient layer (51).
- the low friction coefficient layer (51) can be a fluorinated layer (51a).
- the low friction coefficient layer according to the present invention can be formed. Therefore, since it is not necessary to add facilities and change processes necessary for fluorination treatment to form a low friction coefficient layer, a metal ring having a low friction coefficient layer and a continuously variable transmission provided with the same It is possible to avoid an increase in the manufacturing cost of the belt.
- the fluorination treatment if the fluorination treatment layer is replaced with the nitriding treatment layer if the fluorination treatment is performed before the nitriding treatment, the fluorination treatment is performed by performing the surface treatment by the fluorination treatment after the nitriding treatment.
- the fluorination treatment layer can be reliably formed without the layer replacing the nitriding treatment layer. Therefore, by performing the fluorination treatment after the nitriding treatment, it is possible to form a fluorination treatment layer capable of effectively reducing the friction coefficient of the metal ring in the valley portion of the uneven surface.
- the low friction coefficient layer (51) may be a layer (51b) made of a DLC (Diamond-like Carbon) film.
- the friction coefficient of the metal ring can be effectively reduced by forming a layer made of a DLC film excellent in surface slidability as a low friction coefficient layer in the valley portion of the uneven surface of the metal ring.
- the reference numerals in the parentheses above indicate the reference numerals of the constituent elements in the embodiments described later as an example of the present invention.
- the belt for continuously variable transmission it is possible to achieve both the reduction of the friction coefficient of the metal ring and the improvement of the durability, thereby providing a high strength and highly efficient belt for continuously variable transmission. it can.
- FIG. 1 is a skeleton diagram of a power transmission system of a vehicle equipped with a metal belt type continuously variable transmission according to an embodiment of the present invention. It is a fragmentary perspective view showing a part of metal belt. It is a perspective view which shows the metal ring of innermost periphery.
- FIG. 4A is a plan view of the uneven surface (as viewed from the arrow Y in FIG. 3), and FIG. 4B is a side sectional view of the uneven surface, showing the uneven surface and the low friction coefficient layer formed on the inner circumferential surface of the metal ring. (Z-Z sectional view in FIG. 4A).
- FIG. 7A is a view for explaining the boundary film
- FIG. 7A is a view showing a case where the boundary film is of one type
- FIG. 7B is a view showing a case where the boundary film is of two types.
- FIG. 1 is a skeleton diagram of a power transmission system of a vehicle equipped with a metal belt type continuously variable transmission according to an embodiment of the present invention.
- the input shaft 3 connected to the crankshaft 1 of the engine E via the damper 2 is a metal belt via the starting clutch 4. It is connected to the drive shaft 5 of the continuously variable transmission T.
- the drive pulley (drive pulley) 6 provided on the drive shaft 5 includes a stationary pulley half 7 fixed to the drive shaft 5 and a movable pulley half that can move in and out of the stationary pulley half 7.
- the movable pulley half 8 is urged toward the fixed pulley half 7 by the hydraulic pressure acting on the oil chamber 9.
- a driven pulley (a driven pulley) 11 provided on a driven shaft 10 disposed parallel to the drive shaft 5 is a stationary pulley half 12 fixed to the driven shaft 10 and the stationary pulley half 12.
- the movable pulley half 13 is movable toward the fixed pulley half 12 by the hydraulic pressure acting on the oil chamber 14.
- a metal belt 15 (see FIG. 2) formed by supporting a large number of metal elements 32 is wound around a pair of left and right metal ring assemblies 31 and 31.
- Each metal ring assembly 31 is formed by laminating twelve metal rings 33.
- the number of stacked metal rings 33 is not limited to twelve.
- a drive gear 16 for forward movement and a drive gear 17 for reverse movement are relatively rotatably supported by the driven shaft 10, and the drive gear 16 for forward movement and the drive gear 17 for reverse are selectively connected to the driven shaft 10 by a selector 18. It is possible to combine.
- An output shaft 19 disposed parallel to the driven shaft 10 includes a forward driven gear 20 meshing with the forward drive gear 16 and a reverse driven gear 22 meshing with the reverse drive gear 17 via the reverse idle gear 21. Is fixed.
- the rotation of the output shaft 19 is input to the differential 25 via the final drive gear 23 and the final driven gear 24 and transmitted therefrom to the drive wheels Wr, Wr via the left and right axles 26, 26.
- the driving force of the engine E is transmitted to the driven shaft 10 through the crankshaft 1, the damper 2, the input shaft 3, the starting clutch 4, the drive shaft 5, the drive pulley 6, the metal belt 15 and the driven pulley 11. Ru.
- the driving force of the driven shaft 10 is transmitted to the output shaft 19 via the forward drive gear 16 and the forward driven gear 20 to drive the vehicle forward.
- the driving force of the driven shaft 10 is transmitted to the output shaft 19 via the reverse drive gear 17, reverse idle gear 21 and reverse driven gear 22 to cause the vehicle to reverse.
- the hydraulic pressure acting on the oil chamber 9 of the drive pulley 6 of the metal belt type continuously variable transmission T and the oil chamber 14 of the driven pulley 11 is controlled by the hydraulic control unit U2 operated by a command from the electronic control unit U1.
- the transmission ratio is adjusted steplessly. That is, if the oil pressure acting on the oil chamber 14 of the driven pulley 11 is increased relative to the oil pressure acting on the oil chamber 9 of the drive pulley 6, the groove width of the driven pulley 11 decreases and the effective radius increases. Since the groove width of the drive pulley 6 increases and the effective radius decreases accordingly, the transmission ratio of the metal belt type continuously variable transmission T changes steplessly toward LOW.
- the groove width of the drive pulley 6 decreases and the effective radius increases. Since the groove width of the driven pulley 11 is increased and the effective radius is reduced accordingly, the transmission ratio of the metal belt type continuously variable transmission T changes steplessly toward OD.
- FIG. 2 is a partial perspective view showing a part of the metal belt 15.
- the definitions of the longitudinal direction, the lateral direction, and the radial direction of the metal element 32 used in the present embodiment are shown in FIG.
- the radial direction is defined as the radial direction of the pulleys 6 and 11 (see FIG. 1) with which the metal element 32 abuts, and the side closer to the rotation shaft (drive shaft 5 or driven shaft 10) of the pulleys 6 and 11 is radial direction
- the inner side, the side remote from the rotation axis of the pulleys 6, 11 is the radially outer side.
- the left-right direction is defined as the direction along the rotation axis of the pulleys 6 and 11 with which the metal element 32 abuts
- the front-rear direction is defined as the direction along the traveling direction of the metal element 32 during forward travel of the vehicle.
- the metal element 32 punched out of a metal plate material is positioned between the substantially trapezoidal element main body 34 and the pair of left and right ring slots 35 and 35 in which the metal ring assembly 31 is fitted. And a generally triangular ear 37 connected to the top of the element body 34 via the neck 36.
- a pair of pulley contact surfaces 39, 39 that can contact the drive pulley 6 and the V surfaces 6a, 11a of the driven pulley 11 are formed at both end portions in the left-right direction of the element main body 34.
- main surfaces 40 abutting each other are respectively formed on the front side and the rear side in the advancing direction of the metal element 32, and on the lower side of the main surface 40 on the front side in the advancing direction 42 are formed.
- a convex portion 43f and a concave portion (not shown) which can be fitted to each other are formed on the front and rear surfaces of the ear portion 37.
- saddle surfaces 44, 44 for supporting the inner peripheral surface of the metal ring assembly 31, 31 (inner peripheral surface 33a of the innermost metal ring 33) are formed at the lower edge of the left and right ring slots 35, 35. .
- FIG. 3 is a perspective view showing the inner peripheral surface 33a of the innermost metal ring 33
- FIG. 4 is the uneven surface 38 and the low friction coefficient layer 51 formed on the inner peripheral surface 33a of the innermost metal ring 33
- FIG. 4A is a plan view
- FIG. 4B is a side sectional view.
- the uneven surface 38 which consists of several protrusion part 38a and valley part 38b is formed in the inner peripheral surface 33a of the metal ring 33 of innermost periphery.
- the concavo-convex surface 38 has a structure in which a plurality of mountain-shaped projections 38a extending in a direction oblique to the traveling direction of the metal ring 33 intersect in a mesh shape, and between the projections 38a, compared to the projection 38a. Low valleys 38b are formed. Further, in the uneven surface 38, at least a part of the plurality of protruding portions 38a intersect with a plurality of mountain-shaped protruding portions 38a which are separated in the direction perpendicular to the traveling direction of the metal ring 33 and each linearly extends. It is arranged like. Thus, the whole of the projecting portion 38 a formed on the uneven surface 38 is formed in a mesh shape (mesh shape).
- the metal ring 33 is curved at a portion wound around the drive pulley 6 and the driven pulley 11, and linearly extended at a portion of a chord between the drive pulley 6 and the driven pulley 11. Therefore, a crack is likely to be generated in the vicinity of the tip of the protrusion 38a where the bending stress amplitude is the highest, and the crack generation direction and the growth direction become the left and right direction (the direction orthogonal to the traveling direction of the metal ring 33). In particular, at the intersection of two substantially orthogonal protrusions 38a and 33a, the width of the protrusions 38a and 33a when measured in the traveling direction is wide, so that the lubricity is reduced and cracks easily occur. Become.
- the average contact width w in the left-right direction of the protrusion 38a after the initial wear is made equal to or less than a predetermined dimension, the occurrence of a crack can be prevented.
- the reason is that even if pitching occurs on the top of the narrow protrusion 38a, the pitching does not extend in the depth direction because the width of the top of the protrusion 38a is narrow, and as a result, the shallow pitching does not extend to the metal element 32. This is because it is scraped off by contact with the saddle surface 44 and disappears.
- the width of the projecting portion 38a measured in the direction perpendicular to the traveling direction of the metal ring 33 is narrowed, the width of the projecting portion 38a measured in the traveling direction is also narrowed, so oil film breakage at the top of the projecting portion 38a is difficult to occur. Crack generation itself can be prevented.
- the metal ring 33 and the metal element 32 become familiar with each other, and the average hertz surface pressure decreases to make it difficult to generate pitching.
- the top of the projection 38a is worn and the surface roughness is extremely improved, so that the lubricity is improved and the progress of further abrasion is stopped.
- the dimension and shape of the protrusion 38 a is set such that the average contact width w in the left-right direction of the protrusion 38 a after the initial wear is equal to or less than a predetermined dimension (preferably 16 ⁇ m).
- FIG. 5 is a view for explaining the frictional force due to the differential rotation generated between the adjacent metal rings 33 or between the innermost metal ring 33 and the metal element 32, and a cross section of the metal ring 33 and the metal elements 32. It is a figure (XX arrow sectional drawing of FIG. 2). As shown in the figure, when the metal belt 15 is curved, a plurality of metal rings 33 forming the ring assembly 31 on the outer diameter side (radially outside) of the pitch line (line passing through the locking edge 41) L.
- Differential rotation (slip due to peripheral speed difference) between the adjacent metal rings 33 or between the inner peripheral surface 33a of the innermost metal ring 33 and the saddle surface 44 of the metal element 32 opposed thereto, and A frictional force corresponding to the differential rotation is generated.
- This differential rotation occurs as a differential rotation of an amount corresponding to the distance from the pitch line L.
- the frictional force due to the differential rotation generated between the adjacent metal rings 33 is f, and it is between the inner circumferential surface 33 a of the innermost circumferential metal ring 33 and the saddle surface 44 of the opposing metallic element 32.
- the frictional force due to the resulting differential rotation is F.
- the surface treatment of the surface of the metal ring 33 is performed to reduce the coefficient of friction.
- a low friction coefficient layer 51 having a friction coefficient lower than that of the surface of the protruding portion 38a is formed on the surface of the valley portion 38b in the uneven surface 38 formed on the inner circumferential surface 33a of the metal ring 33 ing.
- the low friction coefficient layer 51 can be a fluorination treatment layer 51a described later or a layer 51b made of a DLC film.
- the boundary layer (boundary film) of the metal ring 33 and the metal element 32 is a double layer (two kinds of boundary films) of the low friction coefficient layer 51 and the layer on the surface of the projecting portion 38a (high friction coefficient layer). It is configured to be).
- FIG. 6 is a view schematically showing a true contact surface by the boundary film between the inner peripheral surface 33a of the innermost metal ring 33 and the saddle surface 44 of the metal element 32 opposed thereto.
- FIG. 7 is a diagram for explaining the boundary film, and FIG. 7A is a diagram showing the case where the boundary film is one type, and FIG. 7B is a diagram showing the case where the boundary film is two types.
- the friction of the metal ring 33 when the boundary film between the inner circumferential surface 33a of the innermost metal ring 33 and the saddle surface 44 of the metal element 32 is only one kind of boundary film M.
- the coefficient ⁇ 1 is expressed by the following (Expression 1).
- friction force F
- vertical load W
- true contact area of boundary film M Ar
- shear strength of boundary film M s.
- the friction coefficient ⁇ 1 of the metal ring 33 is F (frictional force) / W (vertical load), and the frictional force F in this case is Ar (real contact area) ⁇ s (the boundary film M generated by sliding) Shear strength).
- the boundary film (boundary lubricating film) has a different film structure depending on the sliding oil material including the additive of the working oil and the surface treatment, so the shear strength is also different.
- the friction coefficient ⁇ 1 of the metal ring 33 in the case where the boundary film is only one kind of boundary film M depends on the shear strength s of the boundary lubricating film generated by sliding. It will be done.
- the life also depends on the surface treatment of the surface on which the boundary lubricating film is formed, and the surface treatment with a low friction coefficient is not necessarily a long life, and it is necessary to achieve both a low friction coefficient and a long life It will be difficult.
- the boundary film between the inner circumferential surface 33a of the innermost metal ring 33 and the saddle surface 44 of the metal element 32 is the first boundary film M1 and the second boundary
- the friction coefficient ⁇ 2 of the metal ring 33 in the case of two types of films M2 is represented by the following (Expression 2).
- the friction coefficient ⁇ 2 in the case of two types of boundary films is the sum of the two types of friction coefficients, and the ratio of the two types of friction coefficients is the true contact area of each boundary film M1, M2. It depends on the ratio of Ar1 and Ar2. Therefore, by providing two types of boundary layers, ie, the boundary layer formed on the surface of the protrusion 38a that can prevent the occurrence of cracks, and the boundary layer by surface treatment having a low coefficient of friction, the coefficient of friction on the surface can be reduced. It is possible to achieve a long life.
- the boundary layer (boundary film) between the metal ring 33 and the metal element 32 is the low friction coefficient layer 51 and the layer on the surface of the protruding portion 38a (high friction coefficient layer) Of two layers (two types of boundary films).
- FIG. 8 is a view for explaining the process of surface treatment for forming the low friction coefficient layer 51 described above.
- the low friction coefficient layer 51 is formed on the inner circumferential surface 33 a of the innermost metal ring 33 among the plurality of metal rings 33 constituting the metal ring assembly 31 .
- a mesh-like (mesh-like) uneven surface comprising a plurality of projections 38a and valleys 38b on the inner circumferential surface 33a of the metal ring 33.
- a shape corresponding to the uneven surface 38 is formed in advance on the surface (pressing surface) of the rolling roller for rolling the metal ring 33
- the uneven surface 38 is formed on the inner circumferential surface 33 a of the metal ring 33 by rolling the metal ring 33 with a rolling roller.
- the surface of the metal ring 33 is nitrided before the low friction coefficient layer 51 is formed, whereby a nitrided layer 52 is formed as a base layer of the low friction coefficient layer 51 as shown in FIG. 8B.
- the metal ring 33 is subjected to surface treatment for forming the low friction coefficient layer 51, whereby the low friction coefficient layer 51 is formed on the surfaces of the projecting portion 38a and the valley portion 38b as shown in FIG. 8C.
- the low friction coefficient layer 51 can be a fluorinated layer 51 a formed by fluorination treatment of the metal ring 33.
- the fluorination treatment layer 51a can be formed by exposing the metal ring 33 after the nitriding treatment to an atmosphere such as a fluorine source gas.
- the low friction coefficient layer 51 may also be a layer 51 b made of a DLC film.
- the layer 51b made of a DLC film can be formed by various known methods, and either chemical vapor deposition (CVD method) or physical vapor deposition (PVD method) can be used. Alternatively, they may be formed by a method combining the CVD method and the PVD method. In the case of the CVD method, thermal CVD, plasma CVD, etc. are possible. Further, in the case of the PVD method, ion plating, sputtering method and the like are possible.
- the surface of the low friction coefficient layer 51 is worn by sliding with another member and the surface is the same as the surface of the projection 38a. Align to the height. Thereby, as shown to FIG. 8E, the low friction coefficient layer 51 of the surface of the protrusion part 38a is removed, and it will be in the state in which the low friction coefficient layer 51 was formed only in the valley part 38b of the uneven surface 38.
- the low friction coefficient layer 51 of the protrusion 38 a may not be completely removed in this step.
- the low friction coefficient layer 51 is worn by sliding to align its surface at the same height position as the surface of the projecting portion 38a. It is desirable that the film thickness be equal to or less than the thickness dimension of the uneven surface 33 (mesh surface) (the height dimension of the projecting portion 38 a with respect to the valley portion 38 b). However, other than that, the film thickness of the low friction coefficient layer 51 is made thicker than the thickness dimension of the concavo-convex surface 33, and the low friction coefficient rises higher than the projecting portion 38a in the process of using the metal belt 15.
- the layer 51 may be worn by sliding and the surface of the low friction coefficient layer 51 may be equal to or less than the thickness of the uneven surface 33. However, in this case, it is necessary to prevent the low friction coefficient layer 51 formed in the valley portion 38b from peeling off by sliding.
- the surface treatment by fluorination treatment is performed after nitriding treatment, in the case of fluorination treatment, if the fluorination treatment is performed before nitriding treatment, the fluorination treatment layer is replaced with the nitriding treatment layer It is.
- the fluorination treatment after the nitriding treatment instead of the fluorination treatment as the pretreatment of the nitriding treatment in the nitriding treatment, it is possible to form a fluoride layer capable of reducing the friction coefficient in the valley portion 38 b.
- the low friction coefficient layer 51 is the layer 51b made of a DLC film
- the DLC film is formed before the nitriding treatment, the penetration of nitrogen into the base material at the time of the nitriding treatment is hindered or the nitriding treatment is carried out. The heat of this may cause the DLC film to deteriorate.
- the fluorination treatment layer 51a is selected as the low friction coefficient layer 51, the fluorination treatment is performed again as a process after the fluoridation treatment. Therefore, since it is not necessary to add new facilities and change processes for fluorination, an increase in the manufacturing cost of the metal ring 33 and the metal belt 15 can be avoided.
- FIG. 9 is a graph showing a comparison of the power transmission efficiency (belt efficiency) of the metal belt 15 with and without the fluorinated layer 51a.
- the horizontal axis indicates the torque ratio of the metal belt type continuously variable transmission T
- the vertical axis indicates the power transmission efficiency (belt efficiency) of the metal belt 15.
- the torque ratio indicates the ratio of the current input torque to the maximum torque that can be transmitted to the metal belt continuously variable transmission T.
- the power transmission efficiency of the metal belt 15 in which the fluorination treatment layer 51a is formed as the low friction coefficient layer 51 is indicated by a solid line
- the power transmission efficiency of the metal belt 15 in which the fluorination treatment layer 51a is not formed is indicated by a dotted line.
- the frictional resistance is lower than that in the metal belt 15 in which the fluorination treatment layer 51a is not formed. Power transmission efficiency is higher.
- FIG. 10 is a graph showing a comparison of the friction coefficients of the V surfaces 6a and 11a of the pulleys 6 and 11 with and without the fluorinated layer 51a.
- the coefficient of friction between the pulley contact surface 39 of the metal element 32 and the V surfaces 6a and 11a of the pulleys 6 and 11 is desirably desirably a high coefficient of friction in nature
- the fluorination treatment layer 51a is formed as a surface treatment for reducing the friction coefficient of the metal ring 33
- the pulley contact surface 39 of the metal element 32 and the pulleys 6, 11 The coefficient of friction between the V surfaces 6a and 11a is hardly affected.
- the friction of the metal ring 33 is maintained while maintaining the performance required for the metal belt type continuously variable transmission T. By reducing the resistance, high efficiency can be achieved.
- FIG. 11 is a graph showing the power transmission efficiency (belt efficiency) of the metal belt 15 with and without the layer 51b of DLC film.
- the horizontal axis indicates the torque ratio of the metal belt type continuously variable transmission T
- the vertical axis indicates the power transmission efficiency (belt efficiency) of the metal belt 15.
- the power transmission efficiency of the metal belt 15 in which the layer 51b of DLC film is formed as the low friction coefficient layer 51 is indicated by a solid line
- the power transmission efficiency of the metal belt 15 in which the layer 51b of DLC film is not formed is indicated by a dotted line. It shows.
- the frictional resistance of the metal belt 15 is reduced as compared with the case where the layer 51b made of DLC film is not present.
- the power transmission efficiency of the metal belt 15 becomes high.
- the metal ring is formed by the low friction coefficient layer 51 formed in the valley portion 38 b of the uneven surface 38 of the metal ring 33. Since the coefficient of friction 33 can be kept low, the frictional resistance due to the sliding between the metal rings 33 or between the metal ring 33 and the metal element 32 can be reduced. Moreover, by forming the uneven surface 51 having the plurality of protrusions 38a and the plurality of valleys 38b on the surface of the metal ring 33, the average contact in the left-right direction (width direction) of the protrusions 38a after initial wear is obtained.
- the width w By setting the width w to a predetermined dimension, it is possible to prevent the depthwise development of the pitching produced at the top of the projection 38a when the projection 38a is initially worn. As a result, it is possible to prevent the occurrence of a crack in the protruding portion 38 a and to improve the durability of the metal ring 33. Accordingly, it is possible to achieve both the improvement of the durability of the metal ring 33 and the reduction of the frictional resistance, and it is possible to provide a metal belt for a continuously variable transmission which has high strength and high efficiency (high transmission efficiency).
- the frictional resistance generated at the contact point between the inner peripheral surface 33a of the innermost metal ring 33 and the metal element 32 is the largest as the frictional resistance due to differential rotation between members generated inside.
- the uneven surface 38 is formed on the inner circumferential surface 33a of the innermost metal ring 33 among the plurality of metal rings 33, and the valley 38b of the uneven surface 38 is low.
- the fluorination treatment layer 51a formed by the fluorination treatment as the low friction coefficient layer 51 for reducing the friction coefficient of the metal ring 33, it is again performed as a post-process of the nitridation treatment after the fluorination treatment in the nitriding treatment.
- the low friction coefficient layer 51 of the present embodiment can be formed by performing the fluorination treatment of Therefore, the manufacturing cost of the metal ring 33 and the metal belt 15 on which the low friction coefficient layer 51 is formed can be eliminated because there is no need to add equipment or change the process necessary for the fluorination treatment to form the low friction coefficient layer 51. You can avoid the rise of In addition, the manufacturing costs of the metal belt continuously variable transmission T and the vehicle can be reduced.
- the fluorination treatment if the fluorination treatment layer is replaced with the nitriding treatment layer if the fluorination treatment is performed before the nitriding treatment, the fluorination treatment is performed by performing the surface treatment by the fluorination treatment after the nitriding treatment.
- the fluorination treatment layer can be reliably formed without the layer replacing the nitriding treatment layer. Therefore, by performing the fluorination treatment after the nitriding treatment, it is possible to form the fluorination treatment layer 51a capable of effectively reducing the friction coefficient in the valley portion 38b of the uneven surface 38.
- the layer 51b made of a DLC film excellent in surface slidability is formed as the low friction coefficient layer 51 in the valley portion 38b of the uneven surface 38 of the metal ring 33, the friction coefficient of the metal ring 33 is effectively reduced. be able to.
- the mesh-like uneven surface 38 including the plurality of projecting portions 38 a and the valley portions 38 b is formed on the inner peripheral surface 33 a of the innermost metal ring 33. Then, when the protrusions 38a of the uneven surface 38 are initially worn, the average contact width w of the protrusions 38a measured in the direction perpendicular to the direction of travel is equal to or less than a predetermined dimension in the portion where the protrusions 38a do not intersect. To prevent the development of the pitting on the top of the narrow projection 38a in the depth direction and to eliminate the shallow pitting by wear due to contact with the metal element 32, thereby preventing the occurrence of cracks. be able to.
- the width of the projecting portion 38a measured in the direction perpendicular to the traveling direction of the metal ring 33 is narrowed
- the width of the projecting portion 38a measured in the traveling direction is also narrowed, so oil film breakage at the top of the projecting portion 38a is difficult to occur. It also has the effect of preventing the occurrence of cracks. If the metal ring 33 and the metal element 32 soon become fitted, the average Hertz surface pressure decreases and it becomes difficult to generate pitching, and the top of the projecting portion 38a is abraded to improve the surface roughness. The lubricity is improved and the durability of the metal ring 33 is improved.
- the friction coefficient of the metal ring 33 can be reduced by forming the low friction coefficient layer 51 in the valley portion 38 b of the uneven surface 38 as described above.
- the mesh-like uneven surface 38 is formed only on the inner peripheral surface 33a of the innermost metal ring 33, but the uneven surface 38 may be formed of the innermost metal ring It can form in arbitrary surfaces including the outer peripheral surface of 33, the inner peripheral surface of the other metal ring 33, or the outer peripheral surface.
- the specific shape of the uneven surface 38 formed on the metal ring 33 is not necessarily limited to the one having the mesh-like protruding portion 38a, but may be another shape.
- the low friction coefficient layer 51 is the fluorinated layer 51a formed by fluorination treatment or the layer 51b formed of a DLC film, but other than this, for example, a solid lubricant such as molybdenum disulfide The same effect can also be obtained by applying the like to the valley portion 38 b of the uneven surface 38.
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Abstract
Description
なお、上記の括弧内の符号は、後述する実施形態における構成要素の符号を本発明の一例として示したものである。
Claims (6)
- 駆動プーリおよび従動プーリ間で駆動力を伝達すべく、複数の金属リングを積層した金属リング集合体に複数の金属エレメントを支持した無段変速機用ベルトであって、
前記金属リングの表面に形成された複数の突出部と該複数の突出部の間に形成された複数の谷部とを有する凹凸面を備え、
前記凹凸面における前記谷部には、表面の摩擦係数が前記突出部の表面の摩擦係数よりも低い低摩擦係数層が形成されている
ことを特徴とする無段変速機用ベルト。 - 前記凹凸面は、前記金属リングの進行方向に対して斜め方向に延びる複数の山脈状の前記突出部が網目状に交差した構成である
ことを特徴とする請求項1に記載の無段変速機用ベルト。 - 前記凹凸面は、前記金属リング集合体を構成する複数の金属リングのうち少なくとも最内周の金属リングの内周面に形成されている
ことを特徴とする請求項1又は2に記載の無段変速機用ベルト。 - 前記低摩擦係数層の下地層として窒化処理層が形成されている
ことを特徴とする請求項1乃至3のいずれか1項に記載の無段変速機用ベルト。 - 前記低摩擦係数層は、フッ化処理層である
ことを特徴とする請求項1乃至4のいずれか1項に記載の無段変速機用ベルト。 - 前記低摩擦係数層は、DLC膜からなる層である
ことを特徴とする請求項1乃至4のいずれか1項に記載の無段変速機用ベルト。
Priority Applications (3)
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US14/905,366 US20160153524A1 (en) | 2013-07-18 | 2014-07-10 | Continuously variable transmission belt |
CN201480035772.7A CN105339704A (zh) | 2013-07-18 | 2014-07-10 | 无级变速器用带 |
JP2015527274A JPWO2015008692A1 (ja) | 2013-07-18 | 2014-07-10 | 無段変速機用ベルト |
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JP2013149849 | 2013-07-18 |
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JP (1) | JPWO2015008692A1 (ja) |
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CN110337552B (zh) * | 2017-03-03 | 2021-01-15 | 爱信艾达株式会社 | 传动带的单体的设计方法以及传动带 |
CN109595295B (zh) * | 2017-10-03 | 2020-10-30 | 本田技研工业株式会社 | 无级变速器用金属带及其金属环的制造方法 |
NL1043520B1 (en) * | 2019-12-24 | 2021-09-02 | Bosch Gmbh Robert | A flexible ring for a drive belt, a drive belt for a continuously variable transmission including a flexible ring and a method for manufacturing a flexible ring |
Citations (5)
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JPS57205435U (ja) * | 1981-06-24 | 1982-12-27 | ||
JP2007520667A (ja) * | 2003-12-22 | 2007-07-26 | ロベルト ボッシュ ゲゼルシャフト ミト ベシュレンクテル ハフツング | 無段変速機 |
JP2008045573A (ja) * | 2006-08-10 | 2008-02-28 | Nsk Ltd | 転がり摺動部材及びその製造方法並びに転動装置 |
JP2012062539A (ja) * | 2010-09-17 | 2012-03-29 | Air Water Inc | 低摩擦摺動部材 |
JP2012241844A (ja) * | 2011-05-23 | 2012-12-10 | Toyota Motor Corp | 無端金属ベルト及びエレメントの製造方法 |
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JP3522637B2 (ja) * | 2000-03-30 | 2004-04-26 | 本田技研工業株式会社 | 無端金属ベルト |
JP4078126B2 (ja) * | 2002-06-11 | 2008-04-23 | 本田技研工業株式会社 | 無段変速機用ベルト |
JP2011149518A (ja) * | 2010-01-22 | 2011-08-04 | Toyota Motor Corp | 伝動ベルトの製造方法 |
JP5432971B2 (ja) * | 2011-02-15 | 2014-03-05 | 株式会社神戸製鋼所 | 摺動部材およびその製造方法 |
JP5565386B2 (ja) * | 2011-07-19 | 2014-08-06 | トヨタ自動車株式会社 | 伝動ベルト |
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- 2014-07-10 US US14/905,366 patent/US20160153524A1/en not_active Abandoned
- 2014-07-10 CN CN201480035772.7A patent/CN105339704A/zh active Pending
- 2014-07-10 WO PCT/JP2014/068425 patent/WO2015008692A1/ja active Application Filing
- 2014-07-10 JP JP2015527274A patent/JPWO2015008692A1/ja active Pending
Patent Citations (5)
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JPS57205435U (ja) * | 1981-06-24 | 1982-12-27 | ||
JP2007520667A (ja) * | 2003-12-22 | 2007-07-26 | ロベルト ボッシュ ゲゼルシャフト ミト ベシュレンクテル ハフツング | 無段変速機 |
JP2008045573A (ja) * | 2006-08-10 | 2008-02-28 | Nsk Ltd | 転がり摺動部材及びその製造方法並びに転動装置 |
JP2012062539A (ja) * | 2010-09-17 | 2012-03-29 | Air Water Inc | 低摩擦摺動部材 |
JP2012241844A (ja) * | 2011-05-23 | 2012-12-10 | Toyota Motor Corp | 無端金属ベルト及びエレメントの製造方法 |
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US20160153524A1 (en) | 2016-06-02 |
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