WO2024032445A1 - Poulie à courroie pour système de transmission composite - Google Patents

Poulie à courroie pour système de transmission composite Download PDF

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Publication number
WO2024032445A1
WO2024032445A1 PCT/CN2023/110812 CN2023110812W WO2024032445A1 WO 2024032445 A1 WO2024032445 A1 WO 2024032445A1 CN 2023110812 W CN2023110812 W CN 2023110812W WO 2024032445 A1 WO2024032445 A1 WO 2024032445A1
Authority
WO
WIPO (PCT)
Prior art keywords
pulley
belt
friction
transmission system
groove
Prior art date
Application number
PCT/CN2023/110812
Other languages
English (en)
Chinese (zh)
Inventor
汪金芳
Original Assignee
杭州金瀚能源科技有限公司
汪金芳
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 杭州金瀚能源科技有限公司, 汪金芳 filed Critical 杭州金瀚能源科技有限公司
Publication of WO2024032445A1 publication Critical patent/WO2024032445A1/fr

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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
    • F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
    • F16H55/32—Friction members
    • F16H55/36—Pulleys
    • F16H55/38—Means or measures for increasing adhesion
    • 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
    • F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
    • F16H55/32—Friction members
    • F16H55/36—Pulleys
    • F16H55/50—Features essential to rope pulleys

Definitions

  • the invention belongs to the technical field of transmission equipment, and specifically relates to a pulley for a composite transmission system.
  • the transmission belt and the pulley are driven by friction.
  • the diameter ratio of the two pulleys is relatively large for deceleration.
  • the small pulley is the driving pulley
  • the large pulley is the driven pulley
  • the wrapping angle of the large pulley is It is much larger than the wrapping angle of the small pulley, causing slippage of the small pulley.
  • V-shaped transmission belt and pulley (Application No.: 200920307667.0) on May 19, 2010, which provides a friction transmission under normal conditions; it is only used together when slippage occurs.
  • the meshing transmission enables the equipment to operate normally and smoothly, and also increases the service life of the transmission belt.
  • the pulley is made of rigid material and the belt is made of flexible material
  • the belt will deform to a certain extent, causing the teeth of the belt to separate from the teeth of the pulley. Open, and the friction coefficient between the inner wall of the groove and the side of the belt is small, the friction force is small, and the slipping phenomenon still exists.
  • the object of the present invention is to solve the above-mentioned technical problems existing in the prior art and provide a pulley for a composite transmission system.
  • the main body of the pulley is formed by connecting several pulleys.
  • a belt groove is formed between adjacent pulleys.
  • Two adjacent pulleys are The relative cross-section of the belt forms the grooved side that is driven by friction with the belt. Friction grooves are provided on the side of the belt.
  • the present invention adopts the following technical solutions:
  • a pulley for a composite transmission system including: a pulley main body; the pulley main body is formed by connecting several pulley plates. Formed, a belt groove for the belt to fit is formed between two adjacent wheels; the opposite end faces of the two adjacent wheels form the grooved side of the friction transmission, and the friction groove is provided on the side of the belt.
  • the friction groove improves the connection between the belt and the belt.
  • the coefficient of friction between the sides of the groove In the present invention, a plurality of sheaves are connected to form a main body of the pulley, and a belt groove is formed between adjacent sheaves. The relative cross-sections of two adjacent sheaves form a grooved side that is driven by friction with the belt. Friction grooves are provided on the side of the belt.
  • the belt When the pulley is under high power and load working conditions, the belt is deformed due to force, causing the side of the belt to be close to the friction groove on the friction side, thereby greatly increasing the friction coefficient between the belt and the belt groove. Reduce or eliminate belt slippage.
  • the grooved side is an inclined surface.
  • the grooved side is set as an inclined surface to match the side of the belt, so that the grooved side fits on both sides of the belt.
  • the number of slots is 1-20. According to actual production needs, select the corresponding number of slots.
  • friction grooves are arranged radially on the grooved sides. Friction grooves are arranged radially on the side of the belt groove. When the belt is deformed by force and the belt rotates in the belt groove, the friction groove increases the friction coefficient on the side of the belt, thereby eliminating or reducing the phenomenon of belt slippage.
  • the friction groove depth is 0.2mm-5mm. Under the working environment of the pulley, adjust the depth of the friction groove according to the power and load of the pulley, thereby adjusting the friction coefficient between the side of the belt groove and the belt.
  • the width of the friction groove is 0.5mm-10cm. Under the working environment of the pulley, the width of the friction groove is adjusted according to the power and load of the pulley, thereby adjusting the friction coefficient between the side of the belt groove and the belt.
  • the central angle between two adjacent friction grooves is 0.2°-360°.
  • the friction grooves are circumferentially distributed on the side of the groove, which increases the friction coefficient between the belt and the side of the groove after deformation, thereby increasing the friction and reducing or showing the slipping phenomenon between the belt and the pulley.
  • the central angle between two adjacent friction grooves is one of 10°, 30°, 60° and 90°. According to the working environment of the pulley, the greater the power and load of the pulley, the smaller the central angle between two adjacent friction grooves, making the spacing between the friction grooves smaller, thereby increasing the distance between the side of the groove and the belt. The friction coefficient prevents the belt from slipping.
  • the angle between the opposite grooved sides of two adjacent wheels is 20°-60°.
  • the angle between the grooved sides can be adjusted according to the size of the belt so that the grooved sides fit on both sides of the belt.
  • the included angle between the opposite grooved sides of two adjacent wheels is 38°.
  • a belt groove is formed between two adjacent belt groove sides, and the belt is fitted in the belt groove. The friction between the belt and the belt groove side causes the pulley to control the belt for transmission.
  • the angle between opposite grooved sides is preferably 38°.
  • the wheel plate includes an outer wheel plate and an inner wheel plate.
  • Each of the two ends of the pulley body is provided with an outer wheel plate, and the inner wheel plates are evenly distributed between the two outer wheel plates.
  • the inner wheel discs are evenly spaced between the two outer wheel discs. There is a certain distance between the wheel discs according to the size of the belt, thereby forming a belt groove for the belt to fit into. At the same time, the two side walls of the belt groove fit against the belt. both sides.
  • the distance between the friction grooves on both sides of the inner wheel plate is 0.5mm-200mm.
  • the inner wheel piece of the corresponding size can be selected according to actual production needs to facilitate the operation of the pulley.
  • the main body of the pulley is an integrally formed structure. The assembly time of the pulley body is saved, while the structural stability of the pulley body is improved and the structural strength of the pulley body is increased.
  • outer wheel piece and the inner wheel piece are spliced through a connecting structure.
  • the splicing of the outer wheel piece and the inner wheel piece through a connecting structure to form the main body of the pulley is an existing technology and will not be described in this application.
  • V-shaped pulley Application No.: 201210375570. X
  • the center position of the friction groove is used as the center line a, and the corresponding intersection point of the inner ring on the side of the groove is used as the tangent line b.
  • the center line a and the tangent line b form an included angle ⁇ , and the included angle ⁇ is 0.5°-90°.
  • the friction groove is set at an angle to increase the friction coefficient between the belt and the side of the groove.
  • a gear plate is provided between two adjacent wheel plates, and the outer circumferential surface of the tooth plate is provided with meshing teeth at concave and convex intervals.
  • the settings of the gear plate and the meshing teeth realize the meshing transmission with the belt.
  • the teeth of the belt cooperate with the meshing teeth of the gear plate for meshing transmission.
  • the diameter of the tooth plate is smaller than the diameter of the wheel plate.
  • the meshing teeth are arranged in the belt groove, and the belt is fitted in the belt groove, so that the belt groove plays a limiting role on the belt, and at the same time, the friction transmission between the belt and the pulley is ensured.
  • a plurality of sheaves are connected to form a main body of the pulley, and a belt groove is formed between adjacent sheaves.
  • the relative cross-sections of two adjacent sheaves form a grooved side that is driven by friction with the belt. Friction grooves are provided on the side of the belt.
  • a tooth plate is provided between two adjacent wheel plates, and the outer circumferential surface of the tooth plate is provided with meshing teeth at concave and convex intervals.
  • the settings of the gear plate and the meshing teeth realize the meshing transmission with the belt.
  • the teeth of the belt cooperate with the meshing teeth of the gear plate for meshing transmission.
  • the diameter of the disc is smaller than the diameter of the wheel disc.
  • the meshing teeth are arranged in the belt groove, and the belt is fitted in the belt groove, so that the belt groove plays a limiting role on the belt, and at the same time, the friction transmission between the belt and the pulley is ensured.
  • Figure 1 is a schematic structural diagram of Embodiment 1 of the present invention.
  • Figure 2 is a front view of the pulley main body in Embodiment 1;
  • Figure 3 is a cross-sectional view of A-A in Figure 2;
  • Figure 4 is an enlarged structural schematic diagram of B in Figure 3;
  • FIG. 5 is a schematic structural diagram of Embodiment 2 of the present invention.
  • Figure 6 is a front view of the pulley body in the second embodiment
  • Figure 7 is a cross-sectional view of C-C in Figure 6;
  • Figure 8 is an enlarged structural schematic diagram of D in Figure 7;
  • Figure 9 is a schematic structural diagram of the pulley body when the central angle of two adjacent friction grooves is 10°;
  • Figure 10 is a schematic structural diagram of the inner wheel when the central angle of two adjacent friction grooves is 10°;
  • Figure 11 is a schematic structural diagram of the pulley body when the central angle of two adjacent friction grooves is 30°;
  • Figure 12 is a schematic structural diagram of the inner wheel when the central angle of two adjacent friction grooves is 30°;
  • Figure 13 is a schematic structural diagram of the pulley body when the central angle of two adjacent friction grooves is 60°;
  • Figure 14 is a schematic structural diagram of the inner wheel when the central angle of two adjacent friction grooves is 60°;
  • Figure 15 is a schematic structural diagram of the pulley body when the central angle of two adjacent friction grooves is 90°;
  • Figure 16 is a schematic structural diagram of the inner wheel when the central angle of two adjacent friction grooves is 90°;
  • 1-pulley body 2-grooved; 3-grooved side; 4-friction groove; 5-outer wheel; 6-inner wheel; 7-gear; 8-meshing teeth; a-center line; b-tangent line; ⁇ -included angle.
  • a pulley for a composite transmission system including: a pulley body 1; the pulley body 1 is formed by connecting several pulleys.
  • a groove 2 for the belt to fit into is formed between two adjacent wheels; the opposite end surfaces of the two adjacent wheels form a grooved side 3 for friction transmission, and the groove side 3 is provided with a friction groove 4, and the friction groove 4 improves the Coefficient of friction between belt and grooved side 3.
  • the grooved side 3 is an inclined surface.
  • the grooved side 3 is set as an inclined surface to match the side of the belt, so that the grooved side 3 fits on both sides of the belt.
  • the number of slots is 1-20.
  • Friction grooves 4 are arranged radially on the grooved side 3 . Friction grooves 4 are arranged radially on the side of the belt groove 3. When the belt is deformed by force and the belt rotates in the belt groove 2, the friction groove 4 increases the friction coefficient on the side of the belt, thus eliminating or reducing the phenomenon of belt slippage. .
  • the depth of friction groove 4 is 0.2mm-5mm. Under the working environment of the pulley, the depth of the friction groove 4 is adjusted according to the power and load of the pulley, thereby adjusting the friction coefficient between the groove side 3 and the belt.
  • the width of the friction groove 4 is 0.5mm-10cm.
  • the width of the friction groove 4 is adjusted according to the power and load of the pulley, thereby adjusting the friction coefficient between the groove side 3 and the belt.
  • the central angle between two adjacent friction grooves 4 is 0.2°-360°. Since the diameter of the driving pulley is small and the wrapping angle between the belt and the driving pulley is small, in order to ensure the contact between the belt and the friction groove 4, the friction groove 4 is controlled by adjusting the central angle between two adjacent friction grooves 4 The tightness can adjust the friction coefficient between the belt and the groove side 3 according to the transmission requirements.
  • the friction grooves 4 are circumferentially distributed on the groove side 3, which increases the friction coefficient between the belt and the groove side 3 after deformation, thereby increasing the friction and reducing or showing the friction between the belt and the pulley. slipping phenomenon.
  • the central angle between two adjacent friction grooves 4 is one of 10°, 30°, 60° and 90°. According to the working environment of the pulley, the greater the power and load of the pulley, the smaller the central angle between two adjacent friction grooves 4, making the distance between the friction grooves 4 smaller, thereby improving the distance between the groove side 3 and the pulley. Friction coefficient between belts to avoid belt slippage.
  • the included angle between the opposite grooved sides 3 on two adjacent wheels is 20°-60°.
  • the angle between the grooved sides 3 can be adjusted according to the size of the belt, so that the grooved sides 3 fit on both sides of the belt.
  • a belt groove 2 is formed between two adjacent belt groove sides 3.
  • the belt is fitted in the belt groove 2.
  • the friction between the belt and the belt groove side 3 causes the pulley to control the belt for transmission.
  • Two adjacent wheels are opposite to each other.
  • the angle between the grooved sides 3 is 38°.
  • the angle between the opposite groove side surfaces 3 is preferably 38°.
  • the pulley includes an outer pulley 5 and an inner pulley 6.
  • the inner sheaves 6 are evenly spaced between the two outer sheaves 5.
  • the two side walls of the belt groove 2 Fits snugly on both sides of the belt.
  • the pulley main body 1 is an integrally formed structure.
  • the assembly time of the pulley main body 1 is saved, while the structural stability of the pulley main body 1 is improved, and the structural strength of the pulley main body 1 is increased.
  • the distance between the friction grooves 4 on both sides of the inner wheel plate 6 is 0.5mm-200mm.
  • the inner wheel piece 6 of the corresponding size can be selected according to actual production needs, thereby facilitating the operation of the pulley.
  • the structure of the second embodiment is basically the same as that of the first embodiment. The difference is that in the second embodiment, the outer wheel plate 5 and the inner wheel plate 6 are spliced through a connecting structure.
  • the outer pulley 5 and the inner pulley 6 are spliced through a connecting structure to form the pulley main body 1, which is an existing technology and will not be described in this application.
  • FIGS 5 to 8 they are the third embodiment of the present invention.
  • the structure of this embodiment is basically the same as that of the first embodiment. The difference is that in the third embodiment, a tooth plate 7 is provided between two adjacent wheels.
  • the outer circumferential surface of the gear plate 7 is provided with meshing teeth 8 at concave and convex intervals.
  • the arrangement of the gear plate 7 and the meshing teeth 8 realizes the meshing transmission with the belt.
  • the diameter of the tooth plate 7 is smaller than the diameter of the wheel plate.
  • the meshing teeth 8 are arranged in the belt groove 2, and the belt is fitted in the belt groove 2, so that the belt groove 2 plays a limiting role for the belt, and at the same time ensures the friction transmission between the belt and the pulley.
  • the fourth embodiment of the present invention As shown in Figure 17 and Figure 18, it is the fourth embodiment of the present invention.
  • the structure of this embodiment is basically the same as that of the first embodiment. The difference is that in the fourth embodiment, the center position of the friction groove 4 is used as the center line a, and the groove is used as the center line a.
  • the corresponding intersection point of the inner circle of side 3 is tangent b, and the included angle ⁇ is formed between the center line a and the tangent b, and the included angle ⁇ is 0.5°-90°.
  • the friction groove 4 is arranged at an angle to increase the friction coefficient between the belt and the groove side 3, thereby reducing or eliminating the slipping phenomenon of the belt.
  • the present invention draws a center line a for the center position of the friction groove in Figures 17 and 18, corresponding to The intersection point of the inner ring of the grooved side surface 3 is a tangent line b.
  • the center line a and the tangent line b are not technical features of the present invention.
  • a belt groove 2 is formed between adjacent sheaves, and the relative sections of two adjacent sheaves form a grooved side 3 that is driven by friction with the belt.
  • the friction groove 4 is provided on the grooved side 3 .

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Pulleys (AREA)
  • Transmissions By Endless Flexible Members (AREA)

Abstract

L'invention concerne une poulie à courroie pour un système de transmission composite. La poulie à courroie comprend un corps de poulie à courroie (1), le corps de poulie à courroie (1) étant formé au moyen de la liaison de plusieurs disques de poulie, et une rainure de courroie (2) pour une courroie à incorporer étant formée entre chaque paire de disques de poulie adjacents ; et des faces d'extrémité opposées de chaque paire de disques de poulie adjacents forment des faces latérales de rainure de courroie (3) pour une transmission par frottement, chaque face latérale de rainure de courroie (3) est pourvue d'évidements de frottement (4), et les évidements de frottement (4) améliorent le coefficient de frottement entre la courroie et les faces latérales de rainure de courroie (3). Lorsque la poulie à courroie se trouve dans des conditions de fonctionnement à haute puissance et à charge élevée, une courroie est sollicitée pour se déformer, de sorte que les faces latérales de la courroie sont étroitement ajustées dans les évidements de frottement (4) dans les faces latérales de frottement, améliorant ainsi considérablement le coefficient de frottement entre la courroie et les rainures de courroie (2), et réduisant ou éliminant le phénomène de glissement de la courroie.
PCT/CN2023/110812 2022-08-11 2023-08-02 Poulie à courroie pour système de transmission composite WO2024032445A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CN202210963390.7 2022-08-11
CN202210963390.7A CN115163786A (zh) 2022-08-11 2022-08-11 一种复合传动系统用带轮

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WO2024032445A1 true WO2024032445A1 (fr) 2024-02-15

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WO (1) WO2024032445A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN115163786A (zh) * 2022-08-11 2022-10-11 杭州金瀚能源科技有限公司 一种复合传动系统用带轮

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JP2001048332A (ja) * 1999-08-05 2001-02-20 Nitta Ind Corp 搬送用プーリ
US20090280940A1 (en) * 2008-05-12 2009-11-12 Jaco Ltd Metal v-belt of continuously variable transmission
CN101832373A (zh) * 2009-03-13 2010-09-15 杭州肯莱特传动工业有限公司 特种传送带及带轮
CN202349132U (zh) * 2011-09-30 2012-07-25 长城汽车股份有限公司 轮径可调的皮带传动机构
CN102927243A (zh) * 2012-09-29 2013-02-13 汪金芳 一种v型带轮
CN203892512U (zh) * 2014-04-05 2014-10-22 天津市兴呈达传动机械配件有限公司 一种耐用劈开皮带轮
CN206257211U (zh) * 2016-11-18 2017-06-16 青岛科技大学 一种摩擦系数各向异性的三角带传动装置
CN207277082U (zh) * 2017-10-19 2018-04-27 浙江凯顺特种纸业有限公司 一种单缸双网造纸机的引纸辊
CN111810599A (zh) * 2020-08-18 2020-10-23 广州艾可米汽车科技股份有限公司 一种钢带式无级变速器
CN213839468U (zh) * 2020-12-07 2021-07-30 佛山市旭扬机械设备有限公司 一种低噪音低震动平板皮带轮
CN115163786A (zh) * 2022-08-11 2022-10-11 杭州金瀚能源科技有限公司 一种复合传动系统用带轮
CN217784159U (zh) * 2022-08-11 2022-11-11 杭州金瀚能源科技有限公司 一种复合传动系统用带轮

Patent Citations (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2001048332A (ja) * 1999-08-05 2001-02-20 Nitta Ind Corp 搬送用プーリ
US20090280940A1 (en) * 2008-05-12 2009-11-12 Jaco Ltd Metal v-belt of continuously variable transmission
CN101832373A (zh) * 2009-03-13 2010-09-15 杭州肯莱特传动工业有限公司 特种传送带及带轮
CN202349132U (zh) * 2011-09-30 2012-07-25 长城汽车股份有限公司 轮径可调的皮带传动机构
CN102927243A (zh) * 2012-09-29 2013-02-13 汪金芳 一种v型带轮
CN203892512U (zh) * 2014-04-05 2014-10-22 天津市兴呈达传动机械配件有限公司 一种耐用劈开皮带轮
CN206257211U (zh) * 2016-11-18 2017-06-16 青岛科技大学 一种摩擦系数各向异性的三角带传动装置
CN207277082U (zh) * 2017-10-19 2018-04-27 浙江凯顺特种纸业有限公司 一种单缸双网造纸机的引纸辊
CN111810599A (zh) * 2020-08-18 2020-10-23 广州艾可米汽车科技股份有限公司 一种钢带式无级变速器
CN213839468U (zh) * 2020-12-07 2021-07-30 佛山市旭扬机械设备有限公司 一种低噪音低震动平板皮带轮
CN115163786A (zh) * 2022-08-11 2022-10-11 杭州金瀚能源科技有限公司 一种复合传动系统用带轮
CN217784159U (zh) * 2022-08-11 2022-11-11 杭州金瀚能源科技有限公司 一种复合传动系统用带轮

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