CN111486206B - Pendulum pin chain bearing large torque and impact load and non-road mobile machine - Google Patents
Pendulum pin chain bearing large torque and impact load and non-road mobile machine Download PDFInfo
- Publication number
- CN111486206B CN111486206B CN202010309514.0A CN202010309514A CN111486206B CN 111486206 B CN111486206 B CN 111486206B CN 202010309514 A CN202010309514 A CN 202010309514A CN 111486206 B CN111486206 B CN 111486206B
- Authority
- CN
- China
- Prior art keywords
- chain
- pin
- swing
- chain plate
- plate
- Prior art date
- Legal status (The legal status 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 status listed.)
- Active
Links
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H9/00—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members
- F16H9/02—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members without members having orbital motion
- F16H9/24—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members without members having orbital motion using chains or toothed belts, belts in the form of links; Chains or belts specially adapted to such gearing
-
- 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
- F16G13/00—Chains
- F16G13/02—Driving-chains
- F16G13/06—Driving-chains with links connected by parallel driving-pins with or without rollers so called open links
-
- 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
- F16G15/00—Chain couplings, Shackles; Chain joints; Chain links; Chain bushes
-
- 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
- F16G15/00—Chain couplings, Shackles; Chain joints; Chain links; Chain bushes
- F16G15/10—Emergency joints or links
-
- 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
- F16G15/00—Chain couplings, Shackles; Chain joints; Chain links; Chain bushes
- F16G15/12—Chain links
-
- 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
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/66—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for continuously variable gearings
- F16H61/662—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for continuously variable gearings with endless flexible members
Abstract
The present invention relates to a pivot pin chain that receives a large torque and an impact load, a continuously variable transmission to which the pivot pin chain is attached, and a power machine to which the continuously variable transmission is attached. The mutual proportional relation and the shape of the components such as the chain link, the chain plate and the swing pin of the swing pin chain are specifically set, and meanwhile, the components matched with the stepless speed change device are specifically set, so that the speed change performance of the stepless speed change device is improved, the bearing capacity of the stepless speed change device is increased, the stepless speed change device is more suitable for high-horsepower machinery, and the technical effects of impact resistance, fatigue life improvement and the like are achieved.
Description
Technical Field
The invention belongs to the field of gearboxes, and particularly relates to a stepless speed change device bearing large torque and impact load.
Background
A CVT transmission device applied to mobile machinery is characterized in that a chain or a steel belt surrounds between a movable cone disk and a fixed cone disk, and the working radius of the contact point of the chain or the steel belt and the cone disks is adjusted by changing the distance between the two cone disks, so that the speed change is realized. The transmission ratio of the gearbox is stable, the design and the manufacture are simple and convenient, the speed change range is wide, at present, a plurality of reports are applied to the field of automobiles, and the input torque is below 400 N.m. Non-road mobile machines, such as agricultural machines and construction machines, have a wide range of operation, and there is a strong demand for applying a continuously variable transmission, but most of them have large loads, usually much larger than 400n.m (typically 600 and 1200 n.m), and most of them are impact loads.
The core component of the known CVT transmission is a transmission system consisting of a chain or a steel belt and a driving pulley and a driven pulley, and one of the obstacles of a continuously variable transmission bearing large torque and impact load is a chain with higher reliability. CN106051129 "a novel CVT gearbox" discloses that a bent pin axle and a short pin axle are inserted in the link joint through-hole, two pin axles are mutually attached tightly, the side forms the chain structure to the rolling surface, this kind of structure can reduce the noise and the transmission of chain, but in practical application because about the pin axle with the conical pulley contact surface structure asymmetry, easily cause the chain to bear conical pulley axial resultant force slope, unilateral pin axle atress is too big, the life-span descends.
PCT/DE2006/002053 "link chain", PCT/DE2006/001675 "link plate, chain comprising the link plate, and chain transmission and vehicle equipped with the chain transmission constituted by the chain" respectively disclose structures in which the link plate is articulated by an articulation of the link plate by the link chain, and the pitch, the link plate, the mutual structure of the articulations or the mutual dimensional relationship are optimally configured. On this basis, the german LuK company developed LK 2608, LK 2808, LK 3008, LK 3308, and LK 3708 link sheet types of 0.8mm thickness. On one hand, the product does not limit the stop pin, on the other hand, the optimization is suitable for the condition that the load of the passenger car is small and the stress is uniform so as to achieve the overall optimal design and cost, but the design is not suitable for large torque and impact load through experimental verification.
Disclosure of Invention
The invention mainly solves the technical problem of providing a swing pin chain bearing large torque and impact load and a stepless speed change device, and meets the requirements of mobile machinery, particularly non-road mobile machinery, and other power machinery with large torque and impact load operation conditions on the stepless speed change function.
The method is realized by the following technical means:
a high torque and impact load bearing pivot pin chain is composed of a plurality of chain links.
The overall length of the swing pin chain in the working state is a closed loop distributed on a plane, and the overall length of the swing pin chain in the working state comprises an arc section and a straight line section connected with the arc section; in the plane of the pin chain, the side of the concave shape of the pin chain facing the center of the arc segment is called the inner side of the pin chain, and the side of the convex shape of the pin chain facing away from the center of the arc segment is called the outer side of the pin chain.
Each chain link comprises a plurality of chain plates, the chain plates are in a sheet shape, namely the size of one direction is obviously smaller than the sizes of the other two directions, the obviously smaller size is defined as the thickness of the chain plate, the size consistent with the moving direction of the straight-line section of the oscillating pin chain is defined as the length of the chain plate, and the size vertical to the thickness of the chain plate and the length direction of the chain plate is defined as the height of the chain plate.
Each chain plate is provided with 1 or more than 2 through holes in the thickness direction of the chain plate, and two adjacent chain links are connected through a group of swing pins arranged in the through holes.
Each group of the swing pins comprises two swing pins which are same or basically same in shape and are opposite to each other, and two side surfaces of the end parts of the swing pins are parallel to the length direction of the chain plates and are obliquely arranged with a plane formed by the length direction and the height direction.
At least one end of each swing pin of each group of swing pins is provided with a stop pin so as to limit the link plates from falling off from the swing pins.
The length of the stop pin at least one end of each swing pin in the thickness direction of the chain plate is more than or equal to 2mm (preferably more than or equal to 2.5 mm).
In the working state, the difference between the minimum distance between the baffle pin and the link plate in the thickness direction of each group of swing pins and the thickness of all the link plates on the group of swing pins is more than 0.2mm, preferably more than 0.4 mm.
Preferably, in the straight section part in the working state, the projection of more than 90% of the area of the side surface of the swing pin on a plane perpendicular to the length direction of the chain plate is used, and the curvature radius of the obtained projection curve is more than 150mm, preferably more than 180 mm.
Preferably, in the link plate thickness direction, an area of at least 60% of a length of the stopper pin projected on a cross-section perpendicular to the link plate thickness direction is greater than or equal to 0.75mm, preferably greater than or equal to 1.00 mm.
Preferably, the link plate is arranged on the inner side of the swing pin chain of the straight line segment, and the link plate width in the height direction of the link plate at the lowest point of the link plate in the height direction, which is in contact with the swing pin, is more than 4mm, preferably more than 6 mm; the chain plate is arranged on the outer side of the swing pin chain of the straight-line segment, and the width of the chain plate at the highest point of the contact with the swing pin in the height direction of the chain plate is larger than 3mm, preferably larger than 5mm in the height direction of the chain plate.
Preferably, in the straight line segment part in the working state, the side surface of the swing pin intersects with a plane formed by the length direction and the thickness direction of the link plate, and the curvature radius of a cut arc is greater than or equal to 200mm, preferably greater than or equal to 300 mm.
Preferably, the thickness of the link plate is 0.9mm or more, preferably 1.1mm or more.
Preferably, the minimum pitch of the pendulum pin chain is greater than or equal to 9mm, preferably greater than or equal to 12 mm.
A stepless speed change device bearing large torque and impact load comprises a driving fixed cone disc and a driving movable cone disc which are coaxially arranged, a driven fixed cone disc and a driven movable cone disc which are coaxially arranged, and at least 1 pin oscillating chain bearing the large torque and the impact load; the distance between the axes of the driving fixed cone disc, the driving movable cone disc and the driven fixed cone disc and the driven movable cone disc is A, and the distance is called as a center distance A; the pin oscillating chain is clamped among the driving movable cone disc, the driving fixed cone disc, the driven movable cone disc and the driven fixed cone disc; the total length of the pin chain is L, and the total length of the pin chain comprises an arc section and a straight line section, wherein the arc section is clamped and surrounded among the driving movable conical disc, the driving fixed conical disc, the driven movable conical disc and the driven fixed conical disc, and the straight line section is connected with the arc section; the center distance A is not less than 182 mm.
Preferably, the total length L of the pivot pin is >38+ 0.025A.
A non-road moving machine comprises an engine and a continuously variable transmission connected with the engine and bearing large torque and impact load; a multi-gear transmission is connected onto the stepless speed change device bearing large torque and impact load; and a clutch is arranged between the stepless speed change device bearing the large torque and the impact load and the engine, or between the stepless speed change device bearing the large torque and the impact load and the multi-gear transmission or in the multi-gear transmission.
The invention has the following effects:
1, in normal operation of the conical disc type continuously variable transmission, a chain can generate a principle slight deflection. In actual operation, chain deflection is not only theoretical, as the instantaneous torque change caused by impact load during tractor field operation can approach 1 time of the rated engine torque, resulting in instantaneous chain deflection caused by chain elongation and system deformation. The length and the cross section area of the stop pin welded on the swing pin are enhanced, the welding firmness is enhanced, and the stop pin is ensured to be firm in the process of large torque and impact load.
2, because the chain plate has heat treatment deformation, the stop pin keeps a certain distance from the chain plate, the impact on the stop pin when the chain deflects is reduced, and the transmission of large torque under impact load is effectively ensured.
3, through the curvature radius including link joint length direction and link joint direction of height of increase pendulum pin side, reduce the surface pressure of round pin axle and conical disk contact surface, guarantee the contact strength of pendulum pin and conical disk, under big moment of torsion and impact load, can not lead to vice surface damage of friction.
4, besides the pin shaft and the stop pin, the chain plate is also a main bearing part, and according to theoretical analysis, the weak point of strength is the contact side surface of the swing pin and the chain plate. However, as shown in fig. 7, it was found that, under the action of a large torque and an impact load, the deflection of the chain in the arc section causes the most fatigue fracture at the lowest point of the link plate in the height direction of the link plate on the inner side of the link pin chain in the straight section, and the material area (width) of the link plate at this point is increased, so that the fatigue strength of the link plate can be ensured and the fatigue life of the chain can be prolonged.
Compared with the link plate thickness of 0.7mm and 0.8mm in the prior art, experiments show that the link plate thickness is increased to 0.9mm or more under the same chain width, the flatness and consistency of the link plate can be effectively improved, and the fatigue life of the chain under heavy load can be obviously prolonged.
Aiming at the large-torque impact load, the number of pairs of swing pins clamped by a driven fixed cone disc in a swing pin chain can be increased by increasing the diameter of the cone disc, namely increasing the center distance of a cone disc shaft, and simultaneously the tension of the swing pin chain can be effectively reduced, so that the contact stress between the swing pins and the conical surface of the cone disc is reduced, the stress in a chain plate is reduced, and the fatigue life of a system is prolonged.
And 7, the condition that only one end of the swing pin chain is provided with the stop pin is included, so that the production efficiency can be improved, the cost is reduced, and the assembly, the disassembly and the maintenance are convenient.
Through the measures, the invention can ensure the reliable transmission of the working load of more than 1000N.m under the working condition of impact torque represented by agricultural machinery.
Drawings
FIG. 1 is a schematic view of the structure of example 1 of the present invention.
FIG. 2 is a schematic diagram of a straight line segment and a circular arc segment of a side swing pin chain of the continuously variable transmission device in a working state.
Fig. 3 is a schematic view of the top surface structure of the pivot pin chain of the present invention.
Fig. 4 is a schematic side view of the pivot pin chain of the present invention.
Fig. 5 is a partial schematic view of the pin of the present invention.
Fig. 6 is a schematic structural view of the pin shaft cross section on the plane perpendicular to the length direction of the chain plate (plane a-a in fig. 3) in the invention.
Fig. 7 is a link plate contact pressure distribution diagram.
Fig. 8 is a graph showing the change in vehicle conditions under an impact load of comparative example 1.
Fig. 9 is a graph showing the change in vehicle conditions under an impact load in example 1.
Fig. 10 is a graph showing changes in the amount of chain deflection at transmission input torques of 650n.m and 400n.m for example 1 and comparative example 1.
Fig. 11 is a perspective view of the pivot pin chain of the present invention.
The letters used in the figures are used to explain the dimensional relationships already mentioned and have the following meanings:
a: the center distance; l is the chain length of the oscillating pin chain; w is the width of the chain; m is the thickness of the chain plate; b: the length of the chain plate; h is the height of the chain plate; d: pitch; and n is the length of the stop pin in the thickness direction of the chain plate.
All numbers in the drawings:
1. the engine, 2, the initiative fixed cone disc, 3, the initiative movable cone disc, 4, the multi-gear transmission, 5, the clutch, 6, the driven movable cone disc, 7, the oscillating pin chain, 71, the chain link, 711, the chain plate, 7111, the lowest point of contact between the chain plate and the oscillating pin, 72, the pin shaft, 721, the arc section, 73, the stop pin and 8, the driven fixed cone disc.
Detailed Description
Example 1
A non-road mobile mechanical power transmission device comprises an engine and a continuously variable transmission connected with the engine and bearing large torque and impact load, as shown in figure 1, a multi-gear transmission is connected onto the continuously variable transmission; and a clutch is arranged between the stepless speed change device and the multi-gear speed changer.
The stepless speed change device comprises a driving fixed cone disc, a driving movable cone disc, a driven fixed cone disc, a driven movable cone disc and 1 pin swinging chain which are coaxially arranged, wherein the center distances of the driving fixed cone disc, the driving movable cone disc, the driven fixed cone disc and the driven movable cone disc are 220mm, the pin swinging chain is clamped among the driving movable cone disc, the driving fixed cone disc, the driven movable cone disc and the driven fixed cone disc, and power is transmitted through a friction pair formed by an inclined plane on the side surface of the pin swinging chain and a conical surface of the cone disc; as shown in fig. 2 to 4, the rocker pin chain is composed of a plurality of chain links, the overall length of the rocker pin chain in the working state is a closed loop distributed on a plane, and the overall length of the rocker pin chain in the working state comprises an arc section and a straight line section connected with the arc section; in the plane of the pin chain, the side of the concave shape of the pin chain facing the center of the arc segment is called the inner side of the pin chain, and the side of the convex shape of the pin chain facing away from the center of the arc segment is called the outer side of the pin chain.
Every the chain link contains several link joints, and the link joint is the slice, is provided with a link joint thickness direction's through-hole on every link joint, and two adjacent chain links are linked mutually through setting up a set of pendulum pin in the through-hole, and every group pendulum pin includes two pendulum pins that the shape is the same or basically the same and mutually opposite, the slope of two sides of pendulum pin tip uses link joint length direction as the rotation axis to cooperation conical disc conical surface angle.
At least one end of each swing pin of each group of swing pins is provided with a stop pin to limit the link plates from falling off from the swing pins, as shown in fig. 5. The length of the stop pin in the thickness direction of the chain plate is 2.5 mm; when the swing pin mechanism works, the difference between the minimum distance between the baffle pins on each group of swing pins in the thickness direction and the thickness of all the chain plates on the group of swing pins is 0.4 mm; in the link plate thickness direction, the stop pin is more than 60% long, and the area of projection on a cross section perpendicular to the link plate thickness direction is greater than 0.8 mm.
Fig. 6 is a schematic cross-sectional view of the pin shaft in a plane perpendicular to the length direction of the link plate (plane a-a in fig. 3). When the swing pin is in a straight line section part in a working state, more than 90% of the area of the side surface of the swing pin is projected on a plane vertical to the length direction of the chain plate, and the curvature radius of the obtained projection curve is more than 150mm (preferably more than 180 mm); in the straight line segment part under the working state, the side surface of the swing pin is intersected with a plane formed by the length direction and the thickness direction of the chain plate, and the curvature radius of a cut arc is more than or equal to 200mm (preferably more than or equal to 300 mm). The pendulum pin model number is marked as number 48-02.
The size of the link plate at the lowest point of the link plate in the height direction of the link plate on the inner side of the swing pin chain of the straight-line segment, which is in contact with the swing pin, is 5mm, the size of the link plate at the outer side of the swing pin chain of the straight-line segment, and the size of the link plate at the highest point of the link plate in the height direction, which is in contact with the swing pin, is 4 mm; the thickness of the chain plate is 1.0 mm. The type mark of the chain plate is 48-01, the minimum pitch of the swing pin chain is 10mm, and the width of the chain is 48 mm.
Comparative example 1
The comparative example adopts the power transmission device consistent with the embodiment 1, realizes better comparative operation by replacing the chain, has the center distance of the swing pin chain of 220mm, the length of the stop pin in the thickness direction of the chain plate of 1.0mm, and the difference between the minimum distance between the stop pins on each group of swing pins in the thickness direction of the chain plate and the thickness of all the chain plates on the group of swing pins of 0.2 mm; in the thickness direction of the chain plate, the length of the stop pin is more than 60%, and the area of the projection on the cross section perpendicular to the thickness direction of the chain plate is greater than 0.8 mm; the swing pin is a 48-02 type swing pin consistent with the embodiment 1, the chain plate is a 48-01 type chain plate consistent with the embodiment 1, the minimum pitch of a swing pin chain is 10mm, and the width of the chain is 48 mm. The other settings were the same as in example 1.
The conditions of the transmissions of the examples and comparative examples for the impulsive load were changed as shown in fig. 8 and 9 under the same conditions of the same road and the same engine, in which the rotational speed of the first shaft (continuously variable transmission driving shaft) was maintained at about 1900r/min and the rotational speed of the second shaft (continuously variable transmission driven shaft) was maintained at about 1300 r/min. For comparison, as shown in fig. 8, when an impact load occurs, the output torque of the engine rapidly decreases and then rapidly increases, at this time, the first shaft (the driving shaft of the continuously variable transmission) and the engine are completely combined, the rotating speeds of the engine and the first shaft (the driving shaft of the continuously variable transmission) fluctuate, the rotating speed of the second shaft (the driven shaft of the continuously variable transmission) fluctuates by a small amplitude, after repeated times, the rotating speed of the second shaft (the driven shaft of the continuously variable transmission) is rapidly lost after undergoing small amplitude fluctuation, the output torque of the engine rapidly decreases, the rotating speed of the first shaft (the driving shaft of the continuously variable transmission) rapidly increases and then rapidly decreases, and the chain fails in a box-removing inspection; for the embodiment shown in fig. 9, in the case of impact load, the output torque of the engine rapidly decreases and then rapidly increases, the rotation speeds of the engine and the first shaft (the driving shaft of the continuously variable transmission) fluctuate, the rotation speeds of the second shaft (the driven shaft of the continuously variable transmission) fluctuate slightly, but after repeated times, compared with the comparative example 1, the rotation speeds of the second shaft (the driven shaft of the continuously variable transmission) tend to be stable, the stable stage is also entered in the reaction between the rotation speed of the first shaft (the driving shaft of the continuously variable transmission) and the output torque of the engine, and the chain is found to be intact by unpacking inspection. The amounts of chain deflection at 650n.m and 400n.m input torques for the example and comparative example transmissions were analyzed as shown in fig. 10. If the chain deflection is 0 when the preset speed ratio is 1.3, and the speed ratio is 1.4, the impact load is negative, and the deflection amount of the chain is changed from an alpha point to a beta point in the process that the input torque of the gearbox is changed from 650N.m to 400N.m, so that the deflection amount of the chain is increased. It is explained that not only the aforementioned positive impact load (sharp increase in engine output torque), but also the negative impact load (sharp decrease in engine output torque) causes an increase in the amount of chain skewing.
Example 2
A power transmission device for off-road mobile machinery comprises an engine and a continuously variable transmission connected with the engine and bearing large torque and impact load. The stepless speed change device comprises a driving fixed cone disc, a driving movable cone disc, a driven fixed cone disc, a driven movable cone disc and 1 pin oscillating chain which are coaxially arranged, wherein the center distance between the driving fixed cone disc and the driven fixed cone disc and the center distance between the driven movable cone disc and the driven movable cone disc are 300mm, the pin oscillating chain is clamped between the driving movable cone disc and the driven fixed cone disc and between the driving fixed cone disc and the driven movable cone disc, and power is transmitted through a friction pair formed by an inclined plane on the side surface of the pin oscillating chain and a conical surface of the cone disc; the whole length of the swing pin chain in the working state is a closed loop distributed on a plane, and comprises an arc section and a straight line section connected with the arc section; in the plane of the pin chain, the side of the concave shape of the pin chain facing the center of the arc segment is called the inner side of the pin chain, and the side of the convex shape of the pin chain facing away from the center of the arc segment is called the outer side of the pin chain.
Each chain link contains several link joints, and the link joint is the slice, is provided with a link joint thickness direction's through-hole on every link joint, and two adjacent chain links are linked mutually through setting up a set of pendulum pin in the through-hole, and every group pendulum pin includes two pendulum pins that the shape is the same or basically the same and mutual opposition, the slope of two sides of pendulum pin tip uses link joint length direction as the rotation axis to cooperation conical disc conical surface angle.
At least one end of each swing pin of each group of swing pins is provided with a stop pin so as to limit the chain plate to fall off from the swing pins, and the length of the stop pin in the thickness direction of the chain plate is 2 mm; when the swing pin mechanism works, the difference between the minimum distance between the baffle pins on each group of swing pins in the thickness direction and the thickness of all the chain plates on the group of swing pins is 0.5 mm; in the link plate thickness direction, the stop pin is more than 60% long, and the area of projection on a cross section perpendicular to the link plate thickness direction is greater than 1.0 mm.
When the swing pin is in a straight line section part in a working state, more than 90% of the area of the side surface of the swing pin is projected on a plane vertical to the length direction of the chain plate, and the curvature radius of the obtained projection curve is more than 150mm (preferably more than 180 mm); in the straight line segment part under the working state, the side surface of the swing pin is intersected with a plane formed by the length direction and the thickness direction of the chain plate, and the curvature radius of a cut arc is more than or equal to 200mm (preferably more than or equal to 300 mm).
The size of the link plate at the lowest point of the link plate in the height direction of the link plate on the inner side of the swing pin chain of the straight-line segment, which is in contact with the swing pin, is 5mm, the size of the link plate at the outer side of the swing pin chain of the straight-line segment, and the size of the link plate at the highest point of the link plate in the height direction, which is in contact with the swing pin, is 4 mm; the thickness of the chain plate is 1.0mm, the minimum pitch of the swing pin chain is 10mm, and the width of the chain is 48 mm.
Compared with the well-known luk chain sheet type 0.8mm thick chain plate, the fatigue life of the embodiment is improved by more than 1000 times compared with the comparative chain plate under the same test condition through the chain plate changing operation.
Claims (9)
1. A pivot pin chain for carrying high torque and impact loads, comprising: the pin oscillating chain is composed of a plurality of chain links;
the overall length of the swing pin chain in the working state is a closed loop distributed on a plane, and the overall length of the swing pin chain in the working state comprises an arc section and a straight line section connected with the arc section; in the plane of the pin chain, one side of the concave shape of the pin chain, which faces the center of the arc section, is called the inner side of the pin chain, and one side of the convex shape of the pin chain, which faces away from the center of the arc section, is called the outer side of the pin chain;
each chain link comprises a plurality of chain plates, the chain plates are in a sheet shape, namely the size in one direction is obviously smaller than the sizes in the other two directions, the obviously smaller size is defined as the thickness of the chain plate, the size consistent with the motion direction of the straight-line section of the oscillating pin chain is defined as the length of the chain plate, and the size vertical to the thickness of the chain plate and the length direction of the chain plate is defined as the height of the chain plate;
each chain plate is provided with 1 or more than 1 through hole in the thickness direction of the chain plate, and two adjacent chain links are connected through a group of swing pins arranged in the through holes;
each group of the swing pins comprises two swing pins which are same or basically same in shape and are opposite to each other, and two side surfaces of the end parts of the swing pins are parallel to the length direction of the chain plate and are obliquely arranged with a plane formed by the length direction and the height direction;
at least one end of each swing pin of each group of swing pins is provided with a stop pin so as to limit the link plates from falling off from the swing pins;
the length of the stop pin at least one end of each swing pin in the thickness direction of the chain plate is more than or equal to 2 mm;
when the swing pin mechanism works, the difference between the minimum distance between the baffle pins on each group of swing pins in the thickness direction and the thickness of all the chain plates on the group of swing pins is more than 0.2 mm;
in the thickness direction of the chain plate, the projection area of the stop pin on the section vertical to the thickness direction of the chain plate is more than or equal to 0.75mm in at least 60 percent of the length2；
The chain plate is arranged on the inner side of the swing pin chain of the straight line segment, and the width of the chain plate in the height direction of the chain plate at the lowest point of the contact with the swing pin in the height direction of the chain plate is more than 4 mm;
the chain plate is arranged on the outer side of the swing pin chain of the straight-line segment, and the width of the chain plate in the height direction of the chain plate at the highest point of contact with the swing pin in the height direction of the chain plate is larger than 3 mm.
2. The high torque and impact load carrying pendulum pin chain of claim 1, wherein: when the straight line section part is in the working state, more than 90% of the area of the side surface of the swing pin is projected on a plane vertical to the length direction of the chain plate, and the curvature radius of the obtained projection curve is more than 150 mm.
3. The pendulum pin chain of claim 1, wherein the side surface of the pendulum pin intersects a plane formed by the link plate in the length direction and the thickness direction at the time of the straight segment portion in the operating state, and the radius of curvature of the resulting arc is 200mm or more.
4. The high torque and impact load carrying swing pin chain of claim 1 wherein the link plate thickness is 0.9mm or greater.
5. The link chain of claim 1, wherein the link chain minimum pitch is greater than or equal to 9 mm.
6. The high torque and impact load carrying pendulum pin chain of claim 1, wherein: the length of the stop pin at least one end of each swing pin in the thickness direction of the chain plate is more than or equal to 2.5 mm;
when the swing pin mechanism works, the difference between the minimum distance between the baffle pins on each group of swing pins in the thickness direction and the thickness of all the chain plates on the group of swing pins is more than 0.4 mm;
in the thickness direction of the chain plate, the projection area of the stop pin on the section vertical to the thickness direction of the chain plate is more than or equal to 1.00mm in at least 60 percent of the length of the stop pin2；
When the straight line section part is in a working state, more than 90% of the area of the side surface of the swing pin is projected on a plane vertical to the length direction of the chain plate, and the curvature radius of the obtained projection curve is larger than 180 mm;
the chain plate is arranged on the inner side of the swing pin chain of the straight line segment, and the width of the chain plate in the height direction of the chain plate at the lowest point of contact with the swing pin in the height direction of the chain plate is more than 6 mm;
the chain plate is arranged on the outer side of the swing pin chain of the straight-line segment, and the width of the chain plate in the height direction of the chain plate at the highest point of contact with the swing pin in the height direction of the chain plate is more than 5 mm;
when the straight line section part is in a working state, the side surface of the swing pin is intersected with a plane formed by the length direction and the thickness direction of the chain plate, and the curvature radius of the obtained arc line is more than or equal to 300 mm;
the thickness of the chain plate is more than or equal to 1.1 mm;
the minimum pitch of the pendulum pin chain is more than or equal to 12 mm.
7. A continuously variable transmission subjected to large torque and impact load, characterized in that: the high-torque high-impact-resistance pin chain comprises a driving fixed cone disc, a driving movable cone disc, a driven fixed cone disc, a driven movable cone disc and at least 1 high-torque high-impact-resistance pin chain, wherein the driving fixed cone disc and the driving movable cone disc are coaxially arranged, and the high-torque high-impact-resistance pin chain is used for bearing high torque and impact load according to any one of claims 1 to 6; the distance between the axes of the driving fixed cone disc, the driving movable cone disc and the driven fixed cone disc and the driven movable cone disc is A, and the distance is called as a center distance A; the pin oscillating chain is clamped among the driving movable cone disc, the driving fixed cone disc, the driven movable cone disc and the driven fixed cone disc; the total length of the pin chain is L, and the total length of the pin chain comprises an arc section and a straight line section, wherein the arc section is clamped and surrounded among the driving movable conical disc, the driving fixed conical disc, the driven movable conical disc and the driven fixed conical disc, and the straight line section is connected with the arc section;
the center distance A is not less than 182 mm.
8. A continuously variable transmission unit which is subjected to high torque and impact load according to claim 7, wherein: the total length L of the pendulum pin is greater than 38+ 0.025A.
9. A non-road moving machine, characterized in that the non-road moving machine comprises an engine and a continuously variable transmission device connected to the engine and capable of bearing high torque and impact load according to any one of claims 7 to 8; a multi-gear transmission is connected onto the stepless speed change device bearing large torque and impact load; and a clutch is arranged between the stepless speed change device bearing the large torque and the impact load and the engine, or between the stepless speed change device bearing the large torque and the impact load and the multi-gear transmission or in the multi-gear transmission.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202010309514.0A CN111486206B (en) | 2020-04-20 | 2020-04-20 | Pendulum pin chain bearing large torque and impact load and non-road mobile machine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202010309514.0A CN111486206B (en) | 2020-04-20 | 2020-04-20 | Pendulum pin chain bearing large torque and impact load and non-road mobile machine |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN111486206A CN111486206A (en) | 2020-08-04 |
| CN111486206B true CN111486206B (en) | 2021-07-27 |
Family
ID=71812810
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202010309514.0A Active CN111486206B (en) | 2020-04-20 | 2020-04-20 | Pendulum pin chain bearing large torque and impact load and non-road mobile machine |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN111486206B (en) |
Citations (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101341353A (en) * | 2005-12-21 | 2009-01-07 | 卢克摩擦片和离合器两合公司 | Sprocket chain for especially a vehicle drive unit |
| WO2009093117A1 (en) * | 2008-01-21 | 2009-07-30 | Nissan Motor Co., Ltd. | Chain belt and belt type continuously variable transmission |
| JP2009174607A (en) * | 2008-01-23 | 2009-08-06 | Tsubakimoto Chain Co | Silent chain |
| CN104214274A (en) * | 2013-05-31 | 2014-12-17 | 王国斌 | Method for designing chain without welding spot and riveting spot |
| CN105090356A (en) * | 2015-09-01 | 2015-11-25 | 杭州东华链条集团有限公司 | High-wear-resistance silent chain |
| CN204985514U (en) * | 2015-07-22 | 2016-01-20 | 杭州东华链条集团有限公司 | CVT silence chain and gearbox |
| CN105370799A (en) * | 2014-08-08 | 2016-03-02 | 株式会社捷太格特 | Chain Continuously Variable Transmission |
| CN205937762U (en) * | 2016-08-11 | 2017-02-08 | 杭州东华链条集团有限公司 | Novel CVT gearbox |
| CN108167390A (en) * | 2015-12-18 | 2018-06-15 | 博格华纳公司 | Chain pin keeping method |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6406396B1 (en) * | 2000-12-18 | 2002-06-18 | Hamilton Sundstrand Corporation | Link chain for a continuously variable transmission |
-
2020
- 2020-04-20 CN CN202010309514.0A patent/CN111486206B/en active Active
Patent Citations (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101341353A (en) * | 2005-12-21 | 2009-01-07 | 卢克摩擦片和离合器两合公司 | Sprocket chain for especially a vehicle drive unit |
| WO2009093117A1 (en) * | 2008-01-21 | 2009-07-30 | Nissan Motor Co., Ltd. | Chain belt and belt type continuously variable transmission |
| JP2009174607A (en) * | 2008-01-23 | 2009-08-06 | Tsubakimoto Chain Co | Silent chain |
| CN104214274A (en) * | 2013-05-31 | 2014-12-17 | 王国斌 | Method for designing chain without welding spot and riveting spot |
| CN105370799A (en) * | 2014-08-08 | 2016-03-02 | 株式会社捷太格特 | Chain Continuously Variable Transmission |
| CN204985514U (en) * | 2015-07-22 | 2016-01-20 | 杭州东华链条集团有限公司 | CVT silence chain and gearbox |
| CN105090356A (en) * | 2015-09-01 | 2015-11-25 | 杭州东华链条集团有限公司 | High-wear-resistance silent chain |
| CN108167390A (en) * | 2015-12-18 | 2018-06-15 | 博格华纳公司 | Chain pin keeping method |
| CN205937762U (en) * | 2016-08-11 | 2017-02-08 | 杭州东华链条集团有限公司 | Novel CVT gearbox |
Also Published As
| Publication number | Publication date |
|---|---|
| CN111486206A (en) | 2020-08-04 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| JP2622259B2 (en) | Power transmission chain | |
| US6539700B2 (en) | Chain belt for continuously variable transmission | |
| US8500582B2 (en) | Plate-link chain | |
| US4512754A (en) | Metal chain-belt | |
| US7320656B2 (en) | Plate-link chain | |
| US8485927B2 (en) | Power transmission chain and power transmission device | |
| US8100794B2 (en) | Power transmission chain and power transmission apparatus | |
| CN111486206B (en) | Pendulum pin chain bearing large torque and impact load and non-road mobile machine | |
| EP1258653B1 (en) | CVT chain-belt having wear pads extending from wear links wherein pads are positioned at or between joint/pin ends | |
| CN101809316B (en) | Power transmission chain and power transmission device | |
| US20100035713A1 (en) | Power transmission chain and power transmission device | |
| CN107532683A (en) | Belting and the component for constructing belting | |
| JP5347290B2 (en) | Power transmission chain pretension method | |
| CN212839223U (en) | Continuously variable transmission for small power machinery and single-pin-shaft continuously variable transmission chain applied to continuously variable transmission | |
| CN101631967B (en) | Power transmission chain and power transmission device having the same | |
| CN113825927B (en) | Stamping part for further processing into a chain link for a flat chain and corresponding method for producing a chain link via a stamping process | |
| JP2002349638A (en) | Compression belt for cvt | |
| JP4770454B2 (en) | Method for manufacturing power transmission chain for continuously variable transmission | |
| US8182384B2 (en) | Power transmission chain and power transmission apparatus | |
| WO2011029417A1 (en) | Disk set arrangement for a chain-type cvt | |
| JP4893562B2 (en) | Power transmission chain and power transmission device | |
| CN115003929A (en) | Rocker pin for rocker pin pair of plate link chain | |
| CN112747092A (en) | Diagonal connection steel chain stepless speed changing box | |
| JP2009028737A (en) | Pre-tension applying method and pre-tension applying device for power transmission chain | |
| JP2008168301A (en) | Method and apparatus for manufacturing power transmitting chain |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant |