WO2024185792A1 - 歯付ベルト及び伝動システム - Google Patents

歯付ベルト及び伝動システム Download PDF

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Publication number
WO2024185792A1
WO2024185792A1 PCT/JP2024/008375 JP2024008375W WO2024185792A1 WO 2024185792 A1 WO2024185792 A1 WO 2024185792A1 JP 2024008375 W JP2024008375 W JP 2024008375W WO 2024185792 A1 WO2024185792 A1 WO 2024185792A1
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WO
WIPO (PCT)
Prior art keywords
belt
tooth
toothed
pulley
toothed belt
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PCT/JP2024/008375
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English (en)
French (fr)
Japanese (ja)
Inventor
夢叶 平野
宣考 目木
雅弥 白石
Original Assignee
バンドー化学株式会社
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Publication date
Application filed by バンドー化学株式会社 filed Critical バンドー化学株式会社
Priority to JP2024515719A priority Critical patent/JP7697142B2/ja
Publication of WO2024185792A1 publication Critical patent/WO2024185792A1/ja

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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
    • F16G1/00—Driving-belts
    • F16G1/28—Driving-belts with a contact surface of special shape, e.g. toothed

Definitions

  • the present invention relates to toothed belts and power transmission systems.
  • This application claims priority based on Japanese Application No. 2023-033896 filed on March 6, 2023, and incorporates by reference all of the contents of the above-mentioned Japanese application.
  • a transmission system equipped with a toothed belt and a toothed pulley is known as a power transmission system.
  • a transmission system equipped with a toothed belt can perform stable synchronous transmission with low tension. Therefore, it can be suitably used in general industrial machines such as machine tools and textile machines, and electric power steering devices.
  • the above-mentioned transmission system has a problem in that the sound (running sound) generated during driving becomes noisy.
  • Patent Document 1 proposes a toothed belt capable of reducing noise, which includes a back portion, a plurality of helical teeth arranged in the belt length direction, and a core wire made of fibers that is embedded in the back portion in a spiral shape along the belt length direction, wherein the helical teeth have tooth cloth provided on the inner circumference side, the angle between the direction in which the tooth traces of the helical teeth extend and the belt width direction is 8 degrees or more and 16 degrees or less, the fibers that make up the core wire are made of single-twisted yarn, the twist direction of the yarn is inclined in the opposite direction to the direction in which the tooth traces of the helical teeth extend with respect to the belt width direction, and the winding direction of the core wire is inclined in the same direction as the direction in which the tooth traces of the helical teeth extend with respect to the belt width direction.
  • the present invention was made in consideration of these circumstances, and aims to provide a transmission system with reduced noise.
  • a toothed belt according to the present invention is a toothed belt having a back portion in which a core wire is embedded, and belt teeth provided on the inner peripheral side of the back portion and meshing with a pulley groove of a toothed pulley, a tooth tip compression ratio Y (%) of the belt tooth calculated by the formula (1) is ⁇ 2 ⁇ Y ⁇ 10, A toothed belt, wherein a void ratio X (%) in a tooth width direction of the belt tooth calculated by formula (2) satisfies ⁇ 30 ⁇ X ⁇ 0.
  • This toothed belt has low running noise because the tooth tip compression ratio Y of the belt teeth and the void ratio X of the belt teeth in the tooth width direction are both within a specified range. This toothed belt has reduced noise.
  • the toothed belt of (1) above is It is preferable that the tooth tip compression ratio Y (%) is 0 ⁇ Y ⁇ 8, and the void ratio X (%) is ⁇ 20 ⁇ X ⁇ 10. In this case, the noise can be reduced.
  • the core wire is preferably a carbon core wire or a steel core wire.
  • the toothed belt has good tension maintaining properties, and the belt length of the toothed belt is less likely to change, making it suitable for use in high load transmission applications.
  • the belt teeth are helical teeth
  • the angle of the tooth trace of the helical teeth with respect to the belt width direction is preferably 3 degrees or more and 16 degrees or less. In this case, it is possible to reduce the impact noise generated when the belt teeth and the pulley grooves mesh with each other, thereby further suppressing noise.
  • the ratio B of the thickness Sb of the back portion to the tooth height Hb of the helical teeth is 1.75 or more and 2.40 or less.
  • the toothed belt further suppresses noise, and since the flexural fatigue resistance of the toothed belt is ensured, cracks are less likely to occur on the back surface of the toothed belt.
  • a transmission system is a transmission system having a toothed belt and a toothed pulley that meshes with the toothed belt,
  • the toothed belt is the toothed belt according to any one of (1) to (5).
  • This power transmission system has a toothed belt according to any one of (1) to (5) as a toothed belt, and therefore has low running noise. Noise is suppressed in this power transmission system.
  • FIG. 1 is a side view that illustrates a schematic diagram of a transmission system 1 according to an embodiment of the present invention.
  • the transmission system 1 is suitable for use in general industrial machines such as machine tools, printing machines, textile machines, and injection molding machines, and in electric power steering devices.
  • the transmission system 1 includes a drive pulley 22 , a driven pulley 24 , and a toothed belt 10 .
  • the drive pulley 22 and the driven pulley 24 each have a plurality of pulley grooves 21 formed therein.
  • the toothed belt 10 has a plurality of belt teeth 12 (see FIG. 2 ) on its inner periphery that mesh with the pulley grooves 21.
  • the toothed belt 10 has a core wire 13 embedded therein.
  • the toothed belt 10 is wound around the drive pulley 22 and the driven pulley 24.
  • the drive pulley 22 and driven pulley 24 both have pulley grooves 21 that mesh with the belt teeth 12 of the toothed belt 10 and are evenly spaced along the outer circumference at a predetermined pitch.
  • the pulley grooves 21 of the drive pulley 22 and the pulley grooves 21 of the driven pulley 24 have the same shape.
  • both the drive pulley 22 and the driven pulley 24 will be referred to simply as toothed pulley 20.
  • the transmission system 1 transmits power from a driving source to a driven side.
  • the belt running speed is, for example, 0 rpm or more and 6000 rpm or less.
  • the transmission capacity is, for example, 0.1 kW or more and 10 kW or less.
  • the toothed belt 10 has a plurality of belt teeth 12 on its inner circumferential surface.
  • the pitch Pb of the belt teeth 12 is, for example, not less than 0.50 mm and not more than 3.0 mm.
  • the belt teeth 12 have, for example, a circular arc tooth profile.
  • the toothed pulley 20 is made of, for example, stainless steel.
  • the toothed pulley 20 has pulley grooves 21 that mesh with the belt teeth 12 of the toothed belt 10 and are provided at a predetermined pitch along the outer periphery.
  • the outer diameter of the toothed pulley 20 is, for example, not less than 8 mm and not more than 144 mm.
  • the number of teeth of the toothed pulley 20 is, for example, 10 to 150.
  • the tooth profile of the pulley groove 21 is, for example, a circular arc tooth profile.
  • the toothed pulley 20 may, for example, be provided with a flange.
  • the belt teeth 12 of the toothed belt 10 are configured to smoothly mesh with the pulley grooves 21 .
  • the tooth tip compression ratio Y (%) of the belt tooth 12 and the void ratio X (%) in the tooth width direction of the belt tooth 12 are within specific ranges.
  • the tooth tip compression ratio Y (%) of the belt tooth 12 is an index indicating the compression state of the tooth tip of the belt tooth 12 when the belt tooth 12 meshes with the pulley groove 21.
  • the belt tooth height Hb in formula (1) is the distance between the apex of the tooth tip and the tooth base line in a cross section along the longitudinal direction of the toothed belt 10 (see Hb in FIG. 4).
  • the tooth height Hb of the toothed belt 10 is, for example, not less than 0.50 mm and not more than 2.0 mm.
  • the pulley tooth groove bottom depth Hp in formula (1) is defined by the radial distance between the tooth tip circle Cp and the tooth groove bottom circle Cq in a cross section taken along the circumferential direction of the toothed pulley 20 (see FIG. 5).
  • the tooth groove bottom depth Hp of the toothed pulley 20 is, for example, not less than 0.40 mm and not more than 2.20 mm.
  • the void ratio X (%) of the belt tooth 12 in the tooth width direction is an index showing the amount of backlash when the belt tooth 12 meshes with the pulley groove 21.
  • the belt tooth width ⁇ in formula (2) is the distance between P1 and P2, where P1 and P2 are the intersections between a virtual straight line VL1 that passes through a portion at a height of 1/2 of the belt tooth height Hb in a cross section along the longitudinal direction of the toothed belt 10 and is perpendicular to the direction of the belt tooth height Hb, and the pressure surface of the belt tooth 12.
  • the belt tooth width ⁇ is, for example, not less than 0.50 mm and not more than 3.00 mm.
  • the pulley tooth width ⁇ in formula (2) is the distance between P3 and P4, where P3 and P4 are the intersections between a virtual arc VL2, which is part of a concentric circle of the tooth tip circle Cp and passes through a portion that is half the depth of the pulley tooth groove bottom depth Hp in a cross section along the circumferential direction of the toothed pulley 20, and the tooth flank of the toothed pulley 20.
  • the pulley tooth width ⁇ is, for example, not less than 0.50 mm and not more than 3.00 mm.
  • the toothed belt 10 has a tooth tip compression ratio Y (%) of the belt teeth 12 that satisfies ⁇ 2 ⁇ Y ⁇ 10, and a void ratio X (%) of the belt teeth 12 in the tooth width direction that satisfies ⁇ 30 ⁇ X ⁇ 0.
  • the compression state of the tooth tip of the belt tooth 12 and the amount of backlash when the belt tooth 12 meshes with the pulley groove 21 are set within a predetermined range.
  • the toothed belt 10 can smoothly mesh with the toothed pulley 20. Therefore, the toothed belt 10 can reduce noise.
  • the vibration source refers to a location where meshing impact sound, which is one element of noise, or string vibration sound occurs. The location where the belt teeth 12 and the pulley grooves 21 come into contact with each other when they mesh corresponds to the vibration source.
  • the tooth tip compression ratio Y (%) is less than ⁇ 2, the tooth tips of the toothed belt 10 do not come into contact with the pulley groove 21 when meshing with the toothed pulley. In this case, the vibration source is not dispersed but is concentrated at the tooth bottom portion 15 of the toothed belt 10. Therefore, noise from the transmission system 1 is not sufficiently suppressed. Furthermore, when the tooth tip compression ratio Y (%) exceeds 10, the tooth bottom portion 15 of the toothed belt 10 is in a floating state when meshing with the toothed pulley. In this case as well, the vibration source is not dispersed but is concentrated on the tooth tips of the toothed belt 10. Therefore, noise from the transmission system 1 is not sufficiently suppressed.
  • the toothed belt 10 will experience increased interference on the pressure surface when meshing with the toothed pulley 20. As a result, noise from the transmission system 1 will not be sufficiently suppressed. Furthermore, when the void ratio X (%) is greater than 0, when the toothed belt 10 meshes with the toothed pulley, only the pressure surface on one side of the belt tooth 12 comes into contact with the pulley groove 21. In this case, the vibration source is concentrated on the pressure surface on one side of the belt tooth 12. Therefore, the noise of the transmission system 1 is not sufficiently suppressed.
  • the toothed belt 10 preferably has a tooth tip compression ratio Y (%) of 0 ⁇ Y ⁇ 8 and a void ratio X (%) of ⁇ 20 ⁇ X ⁇ 10.
  • the interference state between the pressure surface of the belt tooth 12 and the tooth surface of the toothed pulley can be made appropriate.
  • the two pressure surfaces of the belt tooth 12 are in contact with the tooth surface of the toothed pulley at the same time, but are not compressed too much. As a result, the noise of the transmission system 1 is further reduced.
  • the tooth tip compression rate Y (%) and the void ratio X (%) satisfy the relationship of formula (3). Y ⁇ -0.45X-4...(3) In this case, the toothed belt 10 is particularly unlikely to generate noise.
  • the belt teeth 12 of the toothed belt 10 are helical teeth.
  • the angle of the tooth trace of the belt teeth 12, which are helical teeth, is preferably 3 degrees or more and 16 degrees or less. In this case, when the toothed belt 10 and the toothed pulley 20 mesh with each other, the belt teeth 12 gradually mesh with the pulley groove 21 from one side to the other along the tooth trace, so that the meshing impact sound can be reduced. Therefore, the noise of the transmission system 1 is suppressed. On the other hand, if the tooth trace angle is less than 3 degrees, the impact noise generated when the teeth mesh with each other is not significantly reduced.
  • the toothed pulley 20 that meshes with the toothed belt 10 also has helical teeth.
  • the ratio B (Sb/Hb) of the thickness Sb of the back portion to the tooth height Hb of the helical teeth is preferably 1.75 or greater and 2.40 or less.
  • the thickness Sb of the back portion is made too thick, the rigidity of the toothed belt 10 becomes too large, and when the toothed belt 10 is wound around the toothed pulley 20, the toothed belt 10 does not mesh well with the pulley groove 21.
  • the toothed belt has a reduced resistance to bending fatigue, which makes the back side and other parts more susceptible to cracking. In particular, cracking occurs more easily in a low-temperature environment.
  • the ratio B (Sb/Hb) is preferably in the above-mentioned range.
  • the toothed belt 10 includes a belt body 11 , a core wire 13 , and a reinforcing fabric 14 .
  • the belt body 11 has a band shape, a base 11a having a rectangular cross section perpendicular to the belt longitudinal direction, and a plurality of teeth 11b provided on the inner periphery of the base 11a.
  • the teeth 11b are integrated with the base 11a.
  • the teeth 11b are provided at equal intervals along the belt length.
  • the reinforcing fabric 14 is provided so as to cover the inner peripheral surface of the toothed portion 11b.
  • the belt tooth 12 is composed of the toothed portion 11b and the reinforcing fabric 14.
  • the belt body 11 is made of, for example, a rubber composition obtained by crosslinking an uncrosslinked rubber composition containing a rubber component and a rubber compounding agent through heating and pressure.
  • the rubber component include hydrogenated nitrile rubber (HNBR), chloroprene rubber (CR), ethylene- ⁇ -olefin elastomers such as ethylene-propylene-diene rubber (EPDM), chlorosulfonated polyethylene rubber, styrene-butadiene rubber, epichlorohydrin rubber, and the like. Of these, HNBR and EPDM are preferred.
  • the rubber compounding agent conventionally known rubber compounding agents can be used, examples of which include a vulcanization accelerator, an antioxidant, a reinforcing agent, a plasticizer, a co-crosslinking agent, and a crosslinking agent.
  • a vulcanization accelerator include metal oxides, metal carbonates, fatty acids and derivatives thereof, etc.
  • the metal oxide include zinc oxide (zinc oxide), magnesium oxide, etc.
  • These vulcanization accelerating aids may be used alone or in combination of two or more kinds. The content of the vulcanization accelerating aid is, for example, 3 parts by mass or more and 15 parts by mass or less per 100 parts by mass of the rubber component.
  • antiaging agent examples include benzimidazole-based antiaging agents, aromatic secondary amine-based antiaging agents, amine-ketone-based antiaging agents, etc. These antiaging agents may be used alone or in combination of two or more kinds.
  • the amount of the antioxidant per 100 parts by mass of the rubber component is, for example, 1.5 parts by mass or more and 3.5 parts by mass or less.
  • Examples of the reinforcing material include carbon black, silica, etc. Carbon black and silica may be used in combination as the reinforcing material. Examples of the carbon black include channel black, furnace black, thermal black, and acetylene black. Examples of the furnace black include SAF, ISAF, N-339, HAF, N-351, MAF, FEF, SRF, GPF, ECF, and N-234. Examples of the thermal black include FT and MT. The carbon black may be used alone or in combination of two or more kinds.
  • the content thereof is, for example, 10 parts by mass or more and 30 parts by mass or less per 100 parts by mass of the rubber component.
  • the content thereof is, for example, 10 parts by mass or more and 30 parts by mass or less per 100 parts by mass of the rubber component.
  • plasticizer examples include dialkyl sebacate, dialkyl phthalate, and dialkyl adipate.
  • dialkyl sebacate examples include polyether ester, dioctyl sebacate (DOS), and the like.
  • dialkyl phthalate examples include dibutyl phthalate (DBP) and dioctyl phthalate (DOP).
  • DBP dibutyl phthalate
  • DOP dioctyl phthalate
  • DOA dioctyl adipate
  • the amount of the plasticizer is, for example, 5 parts by mass or more and 15 parts by mass or less per 100 parts by mass of the rubber component.
  • co-crosslinking agent examples include trimethylolpropane trimethacrylate, m-phenylenedimaleimide, zinc dimethacrylate, triallyl isocyanurate, etc. These co-crosslinking agents may be used alone or in combination of two or more kinds.
  • the amount of the co-crosslinking agent is, for example, 3 parts by mass or more and 8 parts by mass or less based on 100 parts by mass of the rubber component.
  • crosslinking agent examples include sulfur, organic peroxides, etc. Sulfur and organic peroxides may be used in combination. Of course, only one of them may be used. When sulfur and an organic peroxide are used in combination as the crosslinking agent, the total compounding amount of the crosslinking agents is preferably, for example, 0.1 part by mass or more and 0.7 parts by mass or less of sulfur and 1 part by mass or more and 5 parts by mass or less of the organic peroxide, per 100 parts by mass of the rubber component.
  • Examples of the core wire 13 include a glass core wire, an aramid core wire, a carbon core wire, a steel core wire, etc. These core wires are preferably made of twisted yarn.
  • a carbon core wire or a steel core wire is preferable as the core wire 13.
  • Carbon and steel are materials with high elasticity. Therefore, a toothed belt having a carbon core wire or a steel core wire is less likely to change in length when a load is applied, and the change in tooth pitch is small. Therefore, a toothed belt having a carbon core wire or a steel core wire is likely to maintain a good meshing state with a toothed pulley.
  • the outer diameter ⁇ T in the belt thickness direction and the outer diameter ⁇ W in the belt width direction of the core wire 13 are each preferably 0.15 mm to 0.80 mm, more preferably 0.25 mm to 0.50 mm.
  • the outer diameter ⁇ T in the belt thickness direction and the outer diameter ⁇ W in the belt width direction may be the same or different.
  • the core wire 13 has a pitch in the belt width direction and is arranged to form a spiral.
  • the core wire 13 may be composed of two strands, an S-twisted thread and a Z-twisted thread, which are arranged to form a double spiral.
  • the core wires 13 are arranged to extend in parallel with each other at intervals in the belt width direction.
  • the number of the core wires 13 per 10 mm of the belt width is preferably 10 wires/10 mm or more and 26 wires/10 mm or less.
  • the toothed belt 10 having the core wires 13 arranged in this manner is suitable for ensuring excellent durability and excellent tension maintenance in high load transmission.
  • the number of the core wires 13 is more preferably 14 wires/10 mm or more and 24 wires/10 mm or less.
  • the dimension of the gap between adjacent core wires 13 is, for example, not less than 0.1 mm and not more than 0.7 mm.
  • the cords 13 may be subjected to an adhesive treatment to increase the adhesive strength with the belt body.
  • the adhesive treatment include an RFL treatment in which the substrate is immersed in an RFL aqueous solution and then heated, a rubber cement treatment in which the substrate is immersed in rubber cement and then dried, etc. Only one of these adhesive treatments may be performed, or both may be performed.
  • the core wire 13 Prior to the adhesion treatment, the core wire 13 may be subjected to a surface treatment such as immersion in an epoxy solution or an isocyanate solution followed by heating. These adhesion treatments and surface preparations are carried out before winding the core wire around a die in the manufacturing method of the toothed belt described below.
  • the reinforcing fabric 14 is provided so that the direction in which it is easy to stretch coincides with the length direction of the belt.
  • the thickness of the reinforcing fabric 14 is, for example, not less than 0.05 mm and not more than 0.8 mm.
  • FIG. 6 to 8 are diagrams for explaining the manufacturing method of the toothed belt 10. In Fig. 6 to 8, only a part of the belt (including the belt material) and a die 31 for forming the belt are shown.
  • a belt forming die 30 is used.
  • the mold 30 is cylindrical.
  • the outer periphery of the mold 30 is provided with recesses 31 extending in the axial direction and protrusions 32 extending in the axial direction.
  • the recesses 31 are grooves having a cross-sectional shape corresponding to the belt teeth 12 and extending in the axial direction (direction perpendicular to the paper surface of FIG. 6 ).
  • the recesses 31 are provided at a constant pitch and spaced apart in the circumferential direction.
  • the protrusions 32 are provided between adjacent recesses 31.
  • the core wire 12 and the reinforcing cloth 14 are prepared, and if necessary, each is subjected to an adhesive treatment. Furthermore, the reinforcing fabric 14 is formed into a cylindrical shape.
  • a rubber sleeve 34 is placed on the uncrosslinked slab 135 on the mold 31, and the resultant is placed in a vulcanizing can and sealed.
  • high-temperature, high-pressure steam is filled into the vulcanizing can.
  • This state is then maintained for a predetermined time.
  • the uncrosslinked slab 135 is pressed against the mold 31 and heated.
  • the uncrosslinked rubber composition sheet 111 passes between the cords 13 and flows into each of the multiple recesses 32 of the mold 31 while pressing the reinforcing cloth 14, and is crosslinked.
  • the cords 13 and the reinforcing cloth 14 are integrated.
  • a cylindrical belt slab 35 is molded as shown in Fig. 8.
  • the toothed pulley 20 can be manufactured by a conventionally known method.
  • the toothed pulley 20 can be manufactured, for example, by creating a dedicated hob cutter corresponding to the shape of the pulley groove of the toothed pulley, then performing gear cutting processing on a metal material using this hob cutter, and further performing drilling, external processing, flange attachment, etc. as necessary.
  • the belt teeth of the toothed belt according to the embodiment of the present invention are not limited to helical teeth, and may be straight teeth.
  • a pulley having straight teeth on its outer periphery is selected as the toothed pulley.
  • the toothed belt (A) having the same configuration as the toothed belt 10 shown in Figs. 2 to 4 was manufactured.
  • the toothed belt (A) has a belt width Wb of 20 mm and a belt circumference of 330 mm when the compression rate is 0%.
  • the toothed belt (A) has helical teeth with a tooth pitch P of 2 mm and a tooth trace angle of 5 degrees as belt teeth.
  • the toothed belt (A) has a tooth height Hb of 0.76 mm, a total thickness Tb (Hb+Sb) of 2.1 mm, and a belt tooth width ⁇ of 1.044 mm.
  • the belt tooth dimensions of the toothed belt (A) are S 1.3 mm, A 0.172 mm, and r bb 1.3 mm in the belt tooth dimensions shown in Fig. 9.
  • S and r bb correspond to “S” and “ r bb” described in Table 4 of JIS B 1857-1 (2015)
  • A corresponds to "a-Y” derived from Table 4 of JIS B 1857-1 (2015).
  • the rubber component of the belt body 11 is EPDM.
  • the core wire 13 is a carbon core wire. This carbon core wire has an outer diameter ⁇ T in the belt thickness direction and an outer diameter ⁇ W in the belt thickness direction, both of which are 0.33 mm.
  • the reinforcing fabric 14 is a woven fabric. The warp and weft of this woven fabric are made of polyamide 66 fibers.
  • Toothed pulleys (1) to (21) having different shapes of the pulley groove 21 were manufactured.
  • the toothed pulleys (1) to (21) were produced through a manufacturing process including a gear cutting process using a dedicated hob cutter produced according to the shape of the pulley groove of each pulley.
  • the toothed pulleys (1) to (21) each have a tooth tip radius of 12.5 mm and 40 teeth (40T). Two of each of the toothed pulleys (1) to (21) were manufactured.
  • the width of the toothed pulleys (1) to (21) is 22 mm.
  • the toothed pulleys (1) to (21) are made of stainless steel.
  • Examples 1 to 12 Comparative Examples 1 to 9
  • a transmission system was constructed by using the toothed belt, driving pulley and driven pulley in the combinations shown in Tables 1 and 2 and winding the toothed belt around two shaft pulleys having a driving pulley and a driven pulley.
  • FIG. 11 shows the pulley layout of the transmission system.
  • the SW set weight
  • the reduction ratio was 1.0.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Devices For Conveying Motion By Means Of Endless Flexible Members (AREA)
PCT/JP2024/008375 2023-03-06 2024-03-05 歯付ベルト及び伝動システム WO2024185792A1 (ja)

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JP2023-033896 2023-03-06
JP2023033896 2023-03-06

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Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6064354U (ja) * 1983-10-12 1985-05-07 三ツ星ベルト株式会社 歯付ベルトの駆動装置
JP2010060068A (ja) * 2008-09-04 2010-03-18 Gates Unitta Asia Co ベルトシステムおよびベルトシステムの歯付きベルトとプーリ
WO2014024377A1 (ja) * 2012-08-09 2014-02-13 バンドー化学株式会社 歯付ベルト及びこれを備えたベルト減速装置

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0621604B2 (ja) * 1988-01-27 1994-03-23 バンドー化学株式会社 歯付ベルトおよびそのベルトを使用する動力伝達装置
JP5487536B2 (ja) * 2007-07-02 2014-05-07 バンドー化学株式会社 ウレタン製のハス歯ベルト

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6064354U (ja) * 1983-10-12 1985-05-07 三ツ星ベルト株式会社 歯付ベルトの駆動装置
JP2010060068A (ja) * 2008-09-04 2010-03-18 Gates Unitta Asia Co ベルトシステムおよびベルトシステムの歯付きベルトとプーリ
WO2014024377A1 (ja) * 2012-08-09 2014-02-13 バンドー化学株式会社 歯付ベルト及びこれを備えたベルト減速装置

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