CN113653781A - Stepless speed variator - Google Patents
Stepless speed variator Download PDFInfo
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- CN113653781A CN113653781A CN202011580828.0A CN202011580828A CN113653781A CN 113653781 A CN113653781 A CN 113653781A CN 202011580828 A CN202011580828 A CN 202011580828A CN 113653781 A CN113653781 A CN 113653781A
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- 230000005540 biological transmission Effects 0.000 claims abstract description 61
- 230000001105 regulatory effect Effects 0.000 claims description 64
- 229910000831 Steel Inorganic materials 0.000 claims description 24
- 239000010959 steel Substances 0.000 claims description 24
- 238000002347 injection Methods 0.000 claims description 7
- 239000007924 injection Substances 0.000 claims description 7
- 239000011159 matrix material Substances 0.000 claims description 5
- 230000006835 compression Effects 0.000 claims description 4
- 238000007906 compression Methods 0.000 claims description 4
- 230000000052 comparative effect Effects 0.000 description 38
- 238000012360 testing method Methods 0.000 description 13
- 239000000463 material Substances 0.000 description 4
- 238000005728 strengthening Methods 0.000 description 4
- 239000000243 solution Substances 0.000 description 3
- 239000011324 bead Substances 0.000 description 2
- 230000002035 prolonged effect Effects 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 1
- 244000309464 bull Species 0.000 description 1
- 229910052802 copper Inorganic materials 0.000 description 1
- 230000001050 lubricating effect Effects 0.000 description 1
- 229910052759 nickel Inorganic materials 0.000 description 1
- 238000012795 verification Methods 0.000 description 1
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
- F16H37/12—Gearings comprising primarily toothed or friction gearing, links or levers, and cams, or members of at least two of these types
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/04—Features relating to lubrication or cooling or heating
- F16H57/042—Guidance of lubricant
- F16H57/043—Guidance of lubricant within rotary parts, e.g. axial channels or radial openings in shafts
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H9/00—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members
- F16H9/02—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members without members having orbital motion
- F16H9/24—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by endless flexible members without members having orbital motion using chains or toothed belts, belts in the form of links; Chains or belts specially adapted to such gearing
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- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Friction Gearing (AREA)
Abstract
The invention discloses a continuously variable transmission which comprises a first shafting, a second shafting and a transmission element. Through carrying out specific setting to elastic element and each part wherein, improved technical effect such as infinitely variable transmission's system life, transmission efficiency greatly for infinitely variable transmission's great improvement of applicability.
Description
Technical Field
The invention relates to the field of transmissions, in particular to a continuously variable transmission.
Background
The elastic element in the continuously variable transmission is selected to be a disc spring, and the existing elastic element is mainly used for pressurization. Chinese published patent CN110878818A discloses a technical solution of a disc spring as an elastic element, and it is set to have a disc spring stiffness coefficient on a shaft provided with a speed regulating mechanism > a disc spring stiffness coefficient on another shaft. However, such a technical solution causes a large axial pressure, which in turn causes a low efficiency and a reduced system life.
Disclosure of Invention
The invention aims to provide a continuously variable transmission to solve the technical problem in the prior art.
In order to solve the technical problems, the invention provides the following technical scheme:
a kind of stepless speed change gear, including the first shafting, second shafting and drive element, the first shafting includes the first shaft, the first fixed cone disc, the first moves the cone disc, the first elastic element, the first spacing component and the first shafting bearing; the first fixed cone disc is fixedly connected with the first shaft into a whole or is connected with the first shaft in a mode that the first fixed cone disc cannot move axially and cannot rotate relatively (such as a key, a groove and the like); the first movable conical disc and the first fixed conical disc are opposite and coaxially arranged, and the first movable conical disc is connected with the first shaft through a structure (such as a spline, a ball key and the like) which can axially slide but cannot relatively rotate; one end of the first movable conical disc is provided with the first elastic element for pressurization, the first elastic element is a pressurization elastic element, one end of the pressurization elastic element is connected with the first movable conical disc, and the other end of the pressurization elastic element is positioned on the first shaft through the first limiting element (such as a retaining ring or a nut and other structures); the inner diameter of the first elastic element is mounted on the first movable conical disc through clearance fit or mounted on the first shaft through clearance fit; two bearings of a first shaft system are arranged at two ends of the first shaft system, the first shaft system is arranged on the shell through the bearings of the two first shaft systems, a transmission element is clamped between the first fixed cone disc and the first movable cone disc, and the transmission element (preferably a flexible transmission element, particularly a chain or a steel belt and the like) transmits power to the second shaft system.
The second shaft system comprises a second shaft, a second fixed cone disc, a second movable cone disc, a second elastic element, a second limiting element, a bearing of the second shaft system and a speed regulating mechanism; the second fixed cone disc is fixedly connected with the second shaft into a whole, or is connected with the second shaft in a mode that the second fixed cone disc cannot move axially and cannot rotate relatively (such as a key, a groove and the like); the second movable cone disc is connected with the second shaft through a structure (such as a spline, a ball key and the like) which can axially slide but cannot relatively rotate; the transmission element is clamped between the second fixed cone disc and the second movable cone disc to transmit power from the first shafting, the speed regulating mechanism comprises a speed regulating nut and a speed regulating screw rod, the speed regulating nut is connected with the second movable cone disc through a bearing of the second shafting, and the speed regulating screw rod is connected with the second shaft through a bearing of the other second shafting; or the speed regulating screw is connected with the second movable conical disc through a bearing of a second shaft system, and the speed regulating nut is connected with the second shaft through a bearing of the other second shaft system; two bearings of the second shaft system are arranged at two ends of the second shaft, and the second shaft system is arranged on the shell through the bearings of the two second shaft systems.
The second elastic element for reducing the speed regulation force is arranged between the second movable conical disc and the second shaft, one end of the second elastic element is arranged on one side of the second movable conical disc, the other end of the second elastic element is arranged on the second shaft, and the second elastic element is limited by a second limiting element (preferably a check ring or a nut); the first elastic element and the second elastic element have the following relationship: d1 ≧ D2, D1 ≧ D2, t1 ≧ t2, where D1 represents the outer diameter of the first resilient element, D2 represents the outer diameter of the second resilient element, D1 represents the inner diameter of the first resilient element, D2 represents the inner diameter of the second resilient element, t1 represents the thickness of the first resilient element, and t2 represents the thickness of the second resilient element.
The stroke of the first movable conical disc and the second movable conical disc is H, the inclination angle of the first movable conical disc and the second movable conical disc is alpha, the center distance between the first shaft and the second shaft is a, the maximum working radius is R, the minimum working radius is R, the height of the transmission element is H, and the formula is satisfied: h is less than or equal to (2a/3-r) 2tan (alpha).
Alternatively, the second elastic element is not arranged between the second movable cone disc and the second shaft.
Preferably, the first elastic element is a disc spring, or both the first elastic element and the second elastic element are disc springs, wherein the disc spring is made of steel, the matrix element is Fe and contains, by mass percent: c is more than or equal to 0.25 percent and less than or equal to 1 percent, Si is more than or equal to 0.1 percent and less than or equal to 3 percent, Mn is more than or equal to 0.4 percent and less than or equal to 1.5 percent, P is less than or equal to 0.05 percent, Cr is more than or equal to 0.1 percent and less than or equal to 3 percent, Ni is less than or equal to 0.4 percent, and Cu is less than or equal to 0.3 percent.
Alternatively, the speed regulating mechanism comprises a high-speed cam, a low-speed cam and a steel ball, one end of the high-speed cam is mounted on the second shaft through a bearing, the other end of the high-speed cam is provided with a high-speed cam raceway, and the steel ball is arranged in the raceway; one end of the low-speed cam is mounted on the second movable conical disc through a bearing, the other end of the low-speed cam is provided with a low-speed cam raceway, the low-speed cam raceway and a steel ball in the high-speed cam raceway are mounted in a contact manner, a large gear is mounted on the low-speed cam, a small gear is mounted on the high-speed cam and meshed with a small speed regulating gear arranged on a speed regulating shaft, and the small gear is meshed with a speed regulating large gear arranged on the speed regulating shaft; the speed regulating shaft is directly connected with the speed regulating motor, or the speed regulating shaft is connected with the speed regulating motor through a speed reducing mechanism.
Alternatively, an anti-rotation limiting structure for preventing rotation of one of the high-speed cam and the low-speed cam of the speed regulating mechanism is arranged between the other cam and the shell, and the other cam is connected with a speed regulating motor through a speed reducing mechanism.
Preferably, the first elastic element is a disc spring, or the first elastic element and the second elastic element are both disc springs, the disc springs are composed of not less than 3 disc springs, and the number of the disc springs is odd.
The working range of the first elastic element is located in a linear section rather than a straight section in the force value change relationship of the disc spring along with the compression amount.
And a steel wire ring is arranged between each disc spring.
Preferably, the first elastic element is a disc spring, or the first elastic element and the second elastic element are both disc springs, the disc spring is connected with the shaft end of the first movable cone disc and/or the second movable cone disc, and is clamped in a groove on the shaft through 2 semicircular clamping rings for positioning, when the disc spring is in a free state, the inner diameter of the disc spring is d, and the shaft diameter of the first shaft or the second shaft is d0, which satisfies the formula: d is not less than d0+0.02 and is not less than d0+ 0.5.
Preferably, a dynamic balance block or a dynamic balance hole is arranged on the first shaft or the second shaft, and the dynamic balance hole is arranged on an outer cylindrical surface of the outer diameter of the corresponding first fixed cone disc, the second fixed cone disc and/or the first dynamic cone disc and the second dynamic cone disc.
Preferably, the transmission element is a flexible transmission element, specifically a steel belt or a chain, the maximum width of the steel belt or the chain is a0, the outer diameter of the first fixed cone disc, the second fixed cone disc or the first movable cone disc or the second movable cone disc is D0, the center distance between the first shaft and the second shaft is a, and the formula is satisfied: a/3 is more than or equal to A0 is more than or equal to a/10.
Preferably, an oil injection port is arranged at the position of the smallest radius of the conical disc surface facing the first movable conical disc and/or the second movable conical disc, wherein the inner diameter of the oil injection port is di, the center distance between the first shaft and the second shaft is a, and the formula is satisfied: a/100 is not less than di not less than a/300.
Compared with the prior art, the invention has the beneficial effects that:
by using one of the elastic elements for pressurization and setting the elastic element on the other shaft as speed regulation, and simultaneously reducing or canceling the disc spring force value of the shaft provided with the speed regulation screw, the highest efficiency reaches 94%, and in the prior art, the highest efficiency reaches 90%. The force of the disc spring for pressurizing on the first shaft can independently meet the axial force required by the conical disc to transmit power by reasonably limiting the size relation of two elastic elements (preferably the disc spring), and the force of the speed-regulating disc spring is far less than the requirement; and the size relationship between the pressure disc spring and the speed regulation disc spring is limited, so that the force of the pressure disc spring linearly increases along with the increase of the compression amount, and the force of the speed regulation disc spring is kept unchanged or reduced as much as possible when the compression amount is increased. Meanwhile, the speed is regulated faster through the arrangement, and the speed regulation time is prolonged from 8 seconds of the original scheme to 2 seconds of the existing scheme. After the axial force is reduced, the service life of the system is improved by 50 percent compared with the original scheme. Meanwhile, the bearing in the speed regulating mechanism can adopt a one-way stressed bearing, and compared with the two-way stressed bearing of the earliest disc spring patent, the bearing positioning structure is simpler, the number of parts is reduced, the weight is lightened, and the cost is reduced.
Through specific setting of the disc spring material, the cycle life of the disc spring material reaches 200 ten thousand times, and the cycle life of other conventional disc spring materials does not exceed 10 ten thousand times.
The speed regulating mechanism is set in a mode of coordination and matching of the high-speed cam and the low-speed cam, so that a large transmission ratio is realized, meanwhile, the transmission efficiency is 30-40% higher than that of a worm gear, and the efficiency of the worm gear is generally about 30-50%.
The relationship among the stroke of the movable cone disc, the inclination angle of the cone disc and the sizes of the cone discs is set, so that the range of the transmission ratio can be the maximum at present.
Through the number of the disc springs, the stroke is guaranteed, and meanwhile the axial pressing force is guaranteed.
The number of the disc springs is set within the range of the invention in order to ensure the stroke and the service life of the disc springs, so that the structure is the most compact under the condition of ensuring the axial pressure and the stroke. If the number of the disc springs is odd-numbered, the disc springs can be compressed on a shaft with a small diameter in a small diameter mode through a small diameter mode, the disc springs are compressed on a movable conical disc with a large diameter, the movable conical disc can be effectively supported, the thickness of the movable conical disc can be reduced, the weight of a system is reduced, the size of the system is reduced, the deformation of the movable conical disc can be reduced, and the system efficiency can be improved by 1.5-3%.
The pressurizing requirement of the CVT can be met better by reasonably setting the working interval of the disc spring and selecting the disc spring in a linear section (in the prior art, the disc spring is selected in a straight section). The maximum overload of the axial force is not more than 1.5 times, and the maximum overload of the original proposal is 4 times.
The relationship between the inner diameter of the disc spring and the shaft diameter is reasonably set, the centering and dynamic balance after the pressing is ensured, and the maximum vibration of the transmission is reduced by about 10g compared with the original scheme by adopting the formula of the invention. The steel wire rings are arranged between the disc springs to position each other, centering and dynamic balance are guaranteed, and the maximum vibration of the transmission is reduced to 15g compared with that of the original scheme 20g after the structure is adopted.
A dynamic balance block or a dynamic balance hole is arranged on the shaft, and the dynamic balance hole is arranged on the outer cylindrical surface of the outer diameter of the fixed cone disc or the dynamic cone disc. The maximum vibration of the transmission is reduced to 17g compared with the original scheme 20g after the measure is adopted.
By specifically setting the relationship between the maximum width A0 of the chain/steel belt and the center distance a, the structure is more compact and the efficiency is higher under the condition of meeting the requirement of transmission power. The axial distance adopting the formula can be 2a, and the highest efficiency can be 94%; the axial distance of the scheme not adopted can reach 3a, and the highest efficiency is 90%.
An oil outlet is arranged at a specific position where the movable cone disc is farthest away from the fixed cone disc. And a specific formula of the size of the oil outlet is set, so that the oil outlet is set to have the best lubricating effect, and the service life can be obviously prolonged. The verification of the durability by the strengthening test revealed that the above-described arrangement of the present invention after the improvement can increase the durability (durability of the strengthening test) to about 600 hours compared to the durability (durability of the strengthening test) of the prior art of less than 200 hours.
Drawings
Fig. 1 is a schematic structural view of a continuously variable transmission according to an embodiment of the present invention.
Fig. 2 is a schematic structural view of a continuously variable transmission according to another embodiment of the present invention.
Fig. 3 is a schematic structural view of a continuously variable transmission according to a third embodiment of the present invention.
Fig. 4 is a schematic structural view of the high-speed cam or the low-speed cam of the present invention.
Fig. 5 is a side cross-sectional structural schematic view of the disc spring of the present invention.
Wherein the reference numbers in the figures are: 1-a first shaft, 2-a first elastic element, 3-a first limit element, 4-a transmission element, 5-a first movable cone disc, 6-a first fixed cone disc, 7-a bearing of a first shafting, 8-a second movable cone disc, 9-a second fixed cone disc, 10-a second shaft, 11-a speed regulating nut, 12-a bearing of a second shafting, 13-a speed regulating screw, 14-a second elastic element, 15-an anti-rotation limit structure, 16-a bearing of a speed regulating shafting, 17-a speed regulating pinion, 18-a speed regulating shaft, 19-a speed regulating motor, 20-a speed reducing mechanism, 21-a shell, 22-a speed regulating bull gear, 23-a small speed regulating gear, 24-a large speed regulating gear, 25-a low speed cam, 26-a steel ball, 27-a high speed cam, 28-roller path, D-disc spring outer diameter, D-disc spring inner diameter and t-disc spring thickness.
Detailed Description
In order to make the objects, technical solutions and advantages of the present invention more apparent, the present invention is described in further detail below with reference to the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are merely illustrative of the invention and are not intended to limit the invention.
In the description of the present invention, it is to be understood that the terms "longitudinal", "lateral", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", and the like, indicate orientations or positional relationships based on those shown in the drawings, are merely for convenience of description of the present invention, and do not indicate or imply that the referenced devices or elements must have a particular orientation, be constructed and operated in a particular orientation, and thus, are not to be construed as limiting the present invention.
Example 1
Referring to fig. 1, the continuously variable transmission of the present embodiment includes a first shaft system, a second shaft system, a speed adjusting component and a transmission element, wherein the first shaft system includes a first shaft, a first fixed cone disc, a first movable cone disc, a first elastic element, a first limiting element and a bearing of the first shaft system; the first fixed cone disc is connected with the first shaft in a key and groove mode; the first movable conical disc is opposite to the conical surface of the first fixed conical disc and is coaxially arranged, and the first movable conical disc is connected with the first shaft in a key and groove mode; one end of the first movable conical disc is provided with the first elastic element for pressurization, the first elastic element is a pressurization elastic element, one end of the pressurization elastic element is connected with the first movable conical disc, and the other end of the pressurization elastic element is positioned on the first shaft as a first limiting element through a check ring; the first elastic element is arranged on the first shaft in a clearance fit manner; the two ends of the first shaft are provided with two bearings of the first shaft system, the first shaft system is arranged on the shell through the bearings of the two first shaft system, a transmission element is clamped between the first fixed cone disc and the first movable cone disc, the transmission element is a chain, and the transmission element transmits power to the second shaft system.
The second shaft system comprises a second shaft, a second fixed cone disc, a second movable cone disc, a second elastic element, a second limiting element, a bearing of the second shaft system and a speed regulating mechanism; the second fixed cone disc is integrated with the second shaft; the second movable conical disc is connected with the second shaft through a spline; the transmission element is clamped between the second fixed cone disc and the second movable cone disc to transmit power from the first shafting, the speed regulating mechanism comprises a speed regulating nut and a speed regulating screw rod, the speed regulating nut is connected with the second movable cone disc through a bearing of the second shafting, and the speed regulating screw rod is connected with the second shaft or the second shaft through a bearing of the other second shafting; two bearings of the second shaft system are arranged at two ends of the second shaft, and the second shaft system is arranged on the shell through the bearings of the second shaft system.
The second elastic element for reducing the speed regulation force is arranged between the second movable conical disc and the second shaft, one end of the second elastic element is arranged on one side of the second movable conical disc, the other end of the second elastic element is arranged on the second shaft, and the second elastic element is limited through a check ring; the first elastic element and the second elastic element have the following relationship: d1 ≧ D2, D1 ≧ D2, t1 ≧ t2, where D1 represents the outer diameter of the first elastic element, D2 represents the outer diameter of the second elastic element, D1 represents the inner diameter of the first elastic element, D2 represents the inner diameter of the second elastic element, t1 represents the thickness of the first elastic element, and t2 represents the thickness of the second elastic element (the dimensions of the disc spring are shown in FIG. 5). This embodiment is specifically D1 ═ 145, D2 ═ 85, D1 ═ 50, D2 ═ 35, t1 ═ 5.3, and t2 ═ 2.2.
The stroke of the first movable conical disc and the second movable conical disc is H, the inclination angle of the first movable conical disc and the second movable conical disc is alpha, the center distance between the first shaft and the second shaft is a, the maximum working radius is R, the minimum working radius is R, the height of the transmission element is H, and the formula is satisfied: h is less than or equal to (2a/3-r) 2tan (alpha). In this embodiment, H is 16, a is 155, r is 32, and α is 11 °.
The first elastic element and the second elastic element are disc springs, wherein the disc springs are made of steel, the matrix element is Fe and comprises the following components in percentage by mass: c: 0.48%, Si: 0.35%, Mn: 0.62%, P: 0.02%, Cr: 0.93%, Ni: 0.29%, Cu: 0.23 percent
The disc springs are composed of at least 3 disc springs, and the number of the disc springs is odd; in this embodiment, the disc springs are provided with 5 pieces, and a steel wire ring is arranged between each piece of the disc spring.
The dish spring is fixed a position in epaxial inslot through 2 semicircle rand cards at the connection of the axle head of first movable cone dish, and the internal diameter of dish spring is d, and the axle diameter of primary shaft or secondary shaft is d0 when the dish spring is free state, satisfies the formula: d0+0.5 is more than or equal to d0+0.02, and d is 55, and d0 is 49.95 in the embodiment.
And the dynamic balance hole is arranged on the first shaft or the second shaft and is arranged on the outer cylindrical surface of the outer diameters of the corresponding first fixed cone disc, the corresponding second fixed cone disc, the corresponding first movable cone disc and the corresponding second movable cone disc.
The transmission element is a flexible transmission element, in particular to a chain with a guide chain plate, the maximum width of the chain is A0, the diameters of the first fixed cone disk, the second fixed cone disk, the first movable cone disk and the second movable cone disk are D0, the center distance between the first shaft and the second shaft is a, and the formula is satisfied: a/3 is more than or equal to A0 is more than or equal to a/10. This embodiment is specifically a 155, a0 30.2.
The cone disc shaft at the position where the first movable cone disc is farthest from the first fixed cone disc and the cone disc shaft at the position where the second movable cone disc is farthest from the second fixed cone disc are provided with oil injection ports (the embodiment is arranged in the way, in other embodiments, an oil injection pipe can be independently and specially arranged), wherein the inner diameter of each oil injection port is di, the center distance between the first shaft and the second shaft is a, and the formula is satisfied: a/100 is not less than di not less than a/300. In this example, a is 155 and di is 1.2.
Comparative example 1
The comparative example was otherwise set up in the same manner as example 1, except that the requirements of the formulae D1 ≧ D2, D1 ≧ D2, and t1 ≧ t2, specifically D1 ═ 130, D2 ═ 150, D1 ═ 45, D2 ═ 55, t1 ═ 4, and t2 ═ 5.1, were not satisfied, and after comparative testing under the same conditions as example 1, the timing was found to be 2 seconds for example 1, and 8 seconds for the comparative example.
Comparative example 2
The other arrangement modes of the comparative example are the same as those of the example 1, except that the number of the disc springs in the example 1 is 5, and the number of the disc springs in the comparative example is 6, and after comparative tests under the same conditions, the system efficiency of the example 1 is improved by 1.5-3% compared with that of the comparative example.
Comparative example 3
The other arrangement of the present comparative example is the same as that of example 1 except that the disc spring of the first shaft of example 1 is a pressurizing disc spring and the operating range thereof is in a linear section, while the pressurizing disc spring of the present comparative example is arranged in the second shaft, and after comparative tests under the same conditions, it is found that the axial force maximum overload of example 1 is not more than 1.5 times, and the maximum overload of the present comparative example is 4 times.
Comparative example 4
The other arrangement of the comparative example is the same as that of example 1 except that the bead rings are arranged between the disc springs of example 1 and no bead ring is arranged between the disc springs of the comparative example, and it is found that the transmission of example 1 has a maximum vibration of 15g and the transmission of the comparative example has a maximum vibration of 20g after comparative tests under the same conditions.
Comparative example 5
The other arrangement of the comparative example was the same as that of example 1 except that the dynamic balance hole was provided in example 1, whereas the dynamic balance hole was not provided in the comparative example, it was found that the transmission of example 1 had a maximum vibration of 17g and the transmission of the comparative example had a maximum vibration of 20g after comparative tests under the same conditions.
Comparative example 6
The other arrangement modes of the comparative example are the same as the example 1, except that the maximum width of the chain in the example 1 is A0 and the diameter of the conical disc is D0, so that the requirement that the formula a/3 is more than or equal to A0 and more than or equal to a/10 is met, the specific formula a of the comparative example is 130, and the specific formula A0 is 40, and after comparative tests under the same conditions, the axial distance in the example 1 can reach 2a, the highest efficiency can reach 94%, the axial distance in the comparative example can reach 3a, and the highest efficiency is 90%.
Comparative example 7
The other arrangement of the comparative example is the same as that of example 1, except that the example 1 is provided with the oil jet satisfying the specific formula thereof, but the comparative example is not provided with the oil jet, and after the ultrahigh strength contrast test (the ultrahigh torque and ultrahigh rotation speed strengthening test) under the same conditions, it is found that the service life of the continuously variable transmission of example 1 is 600 hours, while the service life of the continuously variable transmission of the comparative example is 200 hours.
Comparative example 8
The other arrangement of the comparative example is the same as that of example 1, except that the content of the material element of the disc spring is different from that of example 1, specifically, the matrix is Fe, and the matrix contains C: 0.23%, Si: 0.35%, Mn: 1.1%, P: 0.02%, Cr: 1.2%, Ti: 0.1%, the cycle life was 10 ten thousand times as compared with 200 ten thousand times for example 1, as determined by a comparative test under the same conditions.
Example 2
Referring to fig. 2, it can be seen that the other components of this embodiment are arranged in the same manner as in embodiment 1, except that the speed adjusting mechanism includes a high-speed cam, a low-speed cam and a steel ball, one end of the high-speed cam is mounted on the second shaft through a bearing, the other end of the high-speed cam is provided with a high-speed cam raceway, and the steel ball is arranged in the raceway; one end of the low-speed cam is mounted on the second movable conical disc through a bearing, the other end of the low-speed cam is provided with a low-speed cam raceway (as shown in fig. 4), the low-speed cam raceway and a steel ball in the high-speed cam raceway are mounted in a contact manner, a large gear (a speed regulation large gear) is mounted on the low-speed cam, a small gear (a speed regulation small gear) is mounted on the high-speed cam, the large gear is meshed with a small speed regulation gear arranged on a speed regulation shaft, and the small gear is meshed with a large speed regulation gear arranged on the speed regulation shaft; is connected with a speed regulating motor through a speed reducing mechanism.
Comparative example 9
The other structures of the comparison example are the same as those of the example 2, and the difference is that the speed regulating mechanism is carried out in a worm gear mode, through a comparative test under the same conditions as the example 2, the transmission efficiency is 30-40% lower than that of the example 2, and the power of the speed regulating motor of the example 2 is 250w, and the power required by the speed regulating motor of the comparison example is 400w to achieve the same speed regulating requirement.
Example 3
Referring to fig. 3, an anti-rotation limiting structure for preventing rotation of one of the high-speed cam and the low-speed cam of the speed regulating mechanism is arranged between the housing and the other cam is connected with a speed regulating motor through a speed reducing mechanism.
Claims (10)
1. A continuously variable transmission characterized in that: comprises a first shaft system, a second shaft system and a transmission element, wherein the first shaft system comprises a first shaft, a first fixed cone disc, a first movable cone disc, a first elastic element, a first limiting element and a bearing of the first shaft system; the first fixed cone disc is fixedly connected with the first shaft into a whole or is connected with the first shaft in a mode that the first fixed cone disc cannot move axially and cannot rotate relatively (such as a key, a groove and the like); the first movable conical disc and the first fixed conical disc are opposite and coaxially arranged, and the first movable conical disc is connected with the first shaft through a structure (such as a spline, a ball key and the like) which can axially slide but cannot relatively rotate; one end of the first movable conical disc is provided with the first elastic element for pressurization, the first elastic element is a pressurization elastic element, one end of the pressurization elastic element is connected with the first movable conical disc, and the other end of the pressurization elastic element is positioned on the first shaft through the first limiting element (such as a retaining ring or a nut and other structures); the inner diameter of the first elastic element is mounted on the first movable conical disc through clearance fit or mounted on the first shaft through clearance fit; two bearings of a first shafting are arranged at two ends of the first shaft, the first shafting is arranged on the shell through the bearings of the two first shafting, a transmission element is clamped between the first fixed conical disc and the first movable conical disc, and the transmission element (preferably a flexible transmission element, particularly a chain or a steel belt and the like) transmits power to the second shafting;
the second shaft system comprises a second shaft, a second fixed cone disc, a second movable cone disc, a second elastic element, a second limiting element, a bearing of the second shaft system and a speed regulating mechanism; the second fixed cone disc is fixedly connected with the second shaft into a whole, or is connected with the second shaft in a mode that the second fixed cone disc cannot move axially and cannot rotate relatively (such as a key, a groove and the like); the second movable cone disc is connected with the second shaft through a structure (such as a spline, a ball key and the like) which can axially slide but cannot relatively rotate; the transmission element is clamped between the second fixed cone disc and the second movable cone disc to transmit power from the first shafting, the speed regulating mechanism comprises a speed regulating nut and a speed regulating screw rod, the speed regulating nut is connected with the second movable cone disc through a bearing of the second shafting, and the speed regulating screw rod is connected with the second shaft through a bearing of the other second shafting; or the speed regulating screw is connected with the second movable conical disc through a bearing of a second shaft system, and the speed regulating nut is connected with the second shaft through a bearing of the other second shaft system; two bearings of a second shaft system are arranged at two ends of the second shaft, and the second shaft system is arranged on the shell through the bearings of the two second shaft systems;
the second elastic element for reducing the speed regulation force is arranged between the second movable conical disc and the second shaft, one end of the second elastic element is arranged on one side of the second movable conical disc, the other end of the second elastic element is arranged on the second shaft, and the second elastic element is limited by a second limiting element (preferably a check ring or a nut); the first elastic element and the second elastic element have the following relationship: d1 is more than or equal to D2, D1 is more than or equal to D2, t1 is more than or equal to t2, wherein D1 represents the outer diameter of the first elastic element, D2 represents the outer diameter of the second elastic element, D1 represents the inner diameter of the first elastic element, D2 represents the inner diameter of the second elastic element, t1 represents the thickness of the first elastic element, and t2 represents the thickness of the second elastic element;
the stroke of the first movable conical disc and the second movable conical disc is H, the inclination angle of the first movable conical disc and the second movable conical disc is alpha, the center distance between the first shaft and the second shaft is a, the maximum working radius is R, the minimum working radius is R, the height of the transmission element is H, and the formula is satisfied: h is less than or equal to (2a/3-r) 2tan (alpha).
2. The variable transmission of claim 1, wherein: alternatively, the second elastic element is not arranged between the second movable cone disc and the second shaft.
3. The variable transmission of claim 1, wherein: the first elastic element is a disc spring, or the first elastic element and the second elastic element are both disc springs, wherein the disc spring is made of steel, the matrix element is Fe according to the mass percentage, and the disc spring comprises: c is more than or equal to 0.25 percent and less than or equal to 1 percent, Si is more than or equal to 0.1 percent and less than or equal to 3 percent, Mn is more than or equal to 0.4 percent and less than or equal to 1.5 percent, P is less than or equal to 0.05 percent, Cr is more than or equal to 0.1 percent and less than or equal to 3 percent, Ni is less than or equal to 0.4 percent, and Cu is less than or equal to 0.3 percent.
4. The variable transmission of claim 1, wherein: alternatively, the speed regulating mechanism comprises a high-speed cam, a low-speed cam and a steel ball, one end of the high-speed cam is mounted on the second shaft through a bearing, the other end of the high-speed cam is provided with a high-speed cam raceway, and the steel ball is arranged in the raceway; one end of the low-speed cam is mounted on the second movable conical disc through a bearing, the other end of the low-speed cam is provided with a low-speed cam raceway, the low-speed cam raceway and a steel ball in the high-speed cam raceway are mounted in a contact manner, a large gear is mounted on the low-speed cam, a small gear is mounted on the high-speed cam and meshed with a small speed regulating gear arranged on a speed regulating shaft, and the small gear is meshed with a speed regulating large gear arranged on the speed regulating shaft; the speed regulating shaft is directly connected with the speed regulating motor, or the speed regulating shaft is connected with the speed regulating motor through a speed reducing mechanism.
5. The variable transmission of claim 4, wherein: alternatively, an anti-rotation limiting structure for preventing rotation of one of the high-speed cam and the low-speed cam of the speed regulating mechanism is arranged between the other cam and the shell, and the other cam is connected with a speed regulating motor through a speed reducing mechanism.
6. The continuously variable transmission of claim 1, or 4 or 5, wherein: the first elastic element is a disc spring, or the first elastic element and the second elastic element are both disc springs, the disc springs are not less than 3 disc springs, and the number of the disc springs is odd;
the working range of the first elastic element is positioned in a linear section rather than a straight section in the change relation of the force value of the disc spring along with the compression quantity;
and a steel wire ring is arranged between each disc spring.
7. The continuously variable transmission of claim 1, or 4 or 5, wherein: the first elastic element is a disc spring, or the first elastic element and the second elastic element are both disc springs, the disc spring is connected with the shaft end of the first movable conical disc and/or the second movable conical disc, the disc spring is positioned in the groove on the shaft through 2 clamping rings, when the disc spring is in a free state, the inner diameter of the disc spring is d, the shaft diameter of the first shaft or the second shaft is d0, and the formula is satisfied: d is not less than d0+0.02 and is not less than d0+ 0.5.
8. The variable transmission of claim 1, wherein: and the first shaft or the second shaft is provided with a dynamic balance block or a dynamic balance hole, and the dynamic balance hole is arranged on the outer cylindrical surface of the outer diameter of the corresponding first fixed cone disc, the second fixed cone disc and/or the first dynamic cone disc and the second dynamic cone disc.
9. The variable transmission of claim 1, wherein: the transmission element is a flexible transmission element, specifically a steel belt or a chain, the maximum width of the steel belt or the chain is A0, the outer diameter of the first fixed cone disc, the second fixed cone disc or the first movable cone disc and the second movable cone disc is D0, the center distance between the first shaft and the second shaft is a, and the formula is satisfied: a/3 is more than or equal to A0 is more than or equal to a/10.
10. The variable transmission of claim 1, wherein: an oil injection port is arranged at the position of the minimum radius of the conical disc surface facing the first movable conical disc and/or the second movable conical disc, the inner diameter of the oil injection port is di, the center distance between the first shaft and the second shaft is a, and the formula is satisfied: a/100 is not less than di not less than a/300.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202011580828.0A CN113653781A (en) | 2020-12-28 | 2020-12-28 | Stepless speed variator |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202011580828.0A CN113653781A (en) | 2020-12-28 | 2020-12-28 | Stepless speed variator |
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| Publication Number | Publication Date |
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| CN113653781A true CN113653781A (en) | 2021-11-16 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202011580828.0A Pending CN113653781A (en) | 2020-12-28 | 2020-12-28 | Stepless speed variator |
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| CN (1) | CN113653781A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114838098A (en) * | 2022-05-10 | 2022-08-02 | 清研华田(南京)农业科技有限公司 | Stepless speed change device and power machine |
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| CN114838098A (en) * | 2022-05-10 | 2022-08-02 | 清研华田(南京)农业科技有限公司 | Stepless speed change device and power machine |
| CN114838098B (en) * | 2022-05-10 | 2024-06-11 | 杭州肇鹏科技有限公司 | Stepless speed change device and power machine |
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