CN114838098A - Stepless speed change device and power machine - Google Patents

Stepless speed change device and power machine Download PDF

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Publication number
CN114838098A
CN114838098A CN202210503125.0A CN202210503125A CN114838098A CN 114838098 A CN114838098 A CN 114838098A CN 202210503125 A CN202210503125 A CN 202210503125A CN 114838098 A CN114838098 A CN 114838098A
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China
Prior art keywords
disc
clutch
driven
driving
cone
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CN202210503125.0A
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Chinese (zh)
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CN114838098B (en
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不公告发明人
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Hangzhou Zhaopeng Technology Co ltd
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Qingyan Huatian Nanjing Agricultural Technology Co ltd
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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
    • C—CHEMISTRY; METALLURGY
    • C22—METALLURGY; FERROUS OR NON-FERROUS ALLOYS; TREATMENT OF ALLOYS OR NON-FERROUS METALS
    • C22C—ALLOYS
    • C22C38/00—Ferrous alloys, e.g. steel alloys
    • C22C38/04—Ferrous alloys, e.g. steel alloys containing manganese
    • C—CHEMISTRY; METALLURGY
    • C22—METALLURGY; FERROUS OR NON-FERROUS ALLOYS; TREATMENT OF ALLOYS OR NON-FERROUS METALS
    • C22C—ALLOYS
    • C22C38/00—Ferrous alloys, e.g. steel alloys
    • C22C38/18—Ferrous alloys, e.g. steel alloys containing chromium
    • C—CHEMISTRY; METALLURGY
    • C22—METALLURGY; FERROUS OR NON-FERROUS ALLOYS; TREATMENT OF ALLOYS OR NON-FERROUS METALS
    • C22C—ALLOYS
    • C22C38/00—Ferrous alloys, e.g. steel alloys
    • C22C38/18—Ferrous alloys, e.g. steel alloys containing chromium
    • C22C38/40—Ferrous alloys, e.g. steel alloys containing chromium with nickel
    • 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
    • F16H—GEARING
    • F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
    • F16H55/02—Toothed members; Worms
    • F16H55/30—Chain-wheels
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/60—Other road transportation technologies with climate change mitigation effect
    • Y02T10/62—Hybrid vehicles

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Materials Engineering (AREA)
  • Metallurgy (AREA)
  • Organic Chemistry (AREA)
  • Friction Gearing (AREA)

Abstract

The present invention relates to a continuously variable transmission and a power machine equipped with the continuously variable transmission. The mutual proportional relation and the shape of components such as chain links, chain plates and swing pins of the swing pin chain are specifically set, and meanwhile, the matched components of 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 road and non-road working conditions, and the technical effects of improving the transmission efficiency, resisting impact, prolonging the fatigue life and the like are achieved.

Description

Stepless speed change device and power machine
Technical Field
The invention belongs to the field of transmissions, and particularly relates to a stepless speed change device.
Background
In a small power machine, no matter a power source is an internal combustion engine or an electric motor, under a plurality of application scenes, a high-efficiency working area of the power source cannot meet the requirement of complex working conditions independently, and a transmission is still required to perform multi-working-condition dynamic adaptation on power.
Continuously variable transmissions have found widespread use in a number of fields due to their unique capabilities of power shifting, without power interruption. The execution process of speed ratio switching (similar to a gear shifting function) is simple, and the speed ratio switching is also suitable for electric driving in the automatic transmission. The main system subfunctions of the conical disc type stepless speed changer are pressurization and speed regulation. The chinese invention publication CN103867678A discloses a conical disc type continuously variable transmission, which is a typical speed regulating system, and the speed regulating system is realized by a speed regulating mechanism of a ball screw structure sleeved on a conical disc shaft and arranged on a movable conical disc. The speed regulating mechanism is better applied to large-torque application such as off-road vehicles due to good rigidity, but has more outstanding problems of higher cost and poorer heat dissipation for medium and small-sized vehicles and other small-torque applications, and particularly has more obvious contradictions between the cost, the weight and the size for the medium and small-sized vehicles with smaller installation space and higher cost requirements.
The Chinese patent publication CN106641143A discloses a cone disc type continuously variable transmission speed regulating mechanism and the cone disc type continuously variable transmission, and the Chinese patent publication CN105972179A discloses a cone disc type continuously variable transmission and a speed regulating mechanism thereof, and the two respectively disclose shifting fork type speed regulating mechanisms, thereby better solving the problems of heat dissipation and lubrication. However, for vehicle applications, the contradiction between the rigidity and the size and weight of the mechanism cannot be uniformly solved. Chinese patent publication CN113653781A discloses a disc spring pressurized continuously variable transmission, but the fully rigid connection of the continuously variable transmission is liable to cause early failure of the system.
Disclosure of Invention
In order to solve the above problems, the present invention provides a continuously variable transmission and a power machine equipped with the continuously variable transmission, which can achieve compact, low-cost, reliable, and efficient characteristics in a small power machine.
In order to achieve the purpose, the invention adopts the following technical scheme:
a stepless speed change device comprises a driving cone disc set, a driven cone disc set, a steel flexible transmission element, a speed regulation device and a cone disc pressurizing device.
The driving cone disc set comprises a driving cone disc shaft, a driving fixed cone disc and a driving movable cone disc, the driving cone disc shaft is fixedly connected with the driving fixed cone disc or is connected in a mode that the driving fixed cone disc cannot rotate and cannot move axially (such as splines, nuts, check rings and the like), the driving movable cone disc comprises a cone with an inner hole and a hollow revolving body (such as a cylinder, a cone and other special-shaped revolving bodies and the like) fixedly connected on the cone, and the driving movable cone disc is connected with the driving cone disc shaft through keys arranged in the inner hole of the cone and the inner hole of the hollow revolving body; and a disc spring or a disc spring group is arranged between the driving cone disc and the driving cone disc shaft, and the disc spring group consists of 2 or more than 2 disc springs.
The driven conical disc set comprises a driven conical disc shaft, a driven fixed conical disc and a driven movable conical disc, the driven conical disc shaft is fixedly connected with the driven fixed conical disc or is connected in a mode that the driven fixed conical disc cannot rotate and cannot axially move (such as a spline, a nut, a check ring and the like), the driven movable conical disc comprises a cone with an inner hole and a hollow revolving body fixedly connected on the cone surface, and the driven movable conical disc is connected with the driven conical disc shaft through a key arranged in the inner hole of the cone and the inner hole of the hollow revolving body; a speed regulating device is arranged between the driven cone disc and the driven cone disc shaft.
The steel flexible transmission element is clamped between the driving fixed cone disc and the driving movable cone disc and between the driven fixed cone disc and the driven movable cone disc at the same time, and is used for transmitting power and motion between the driving cone disc set and the driven cone disc set.
The maximum outer diameter of the driving movable cone disc is D11, the maximum outer diameter of the driving fixed cone disc is D12, the maximum outer diameter of the driven movable cone disc is D21, and the maximum outer diameter of the driven fixed cone disc is D22.
The steel flexible transmission element is a swing pin chain; the oscillating pin chain consists of a plurality of chain links; 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 identical or basically identical in shape and are opposite to each other, and two side faces 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, and the stop pin is used for limiting the chain plate to fall off from the swing pin.
The material of the pin shaft is steel, and in the chemical components of the pin shaft, the content of C is 0.8-1.2 wt%, and the content of Cr is 1.2-1.8 wt%.
The chain plate is made of steel, and the chemical components of the chain plate comprise 0.5-0.8 wt% of C, 0.6-1.2 wt% of Mn, 0.5-0.8 wt% of Cr and 0.3-0.8 wt% of Ni.
The stop pin is made of steel, and the chemical composition of the stop pin contains 0.05-0.4 wt% of C.
The maximum width of the steel flexible transmission element in the direction of the axis of the driving cone shaft is B and meets the requirement.
(D11+D12+D21+D22)/12≥B≥(D11+D12+D21+D22)/60。
In the direction of the axis of the driving cone shaft, the projection area of at least 60 percent of the length of the stop pin on the section perpendicular to the thickness direction of the chain plate is greater than or equal to (D11+ D12+ D21+ D22) 2 /1.5E6。
Or the steel flexible transmission element is a stepless speed change steel belt, the stepless speed change steel belt comprises a plurality of thrust pieces and a belt ring group, each thrust piece comprises at least one open slot, and the open slots are used for accommodating the belt ring group; the belt ring group forms a closed loop by the plurality of thrust plates in the open slot to form a steel flexible transmission element.
The belt ring group consists of a plurality of closed steel rings, and the thickness of each steel ring is 0.07-0.2 mm.
The steel ring is made of maraging steel, and the maraging steel comprises the following chemical components: the carbon content is less than 0.05 wt%.
The thrust piece comprises the following chemical components: the carbon content is 0.8-0.9 wt%, the manganese content is 0.4-0.6 wt%, the sulfur content is less than or equal to 0.03 wt%, the phosphorus content is less than or equal to 0.035 wt%, the chromium content is less than or equal to 0.25 wt%, and the nickel content is less than or equal to 0.20 wt%.
Preferably, the outer edge of one or more of the driving movable conical disc, the driving fixed conical disc, the driven movable conical disc and the driven fixed conical disc is provided with an annular ring, the conical disc provided with the annular ring is defined as an annular ring conical disc, the axis of the annular ring coincides with the axis of the annular ring conical disc, the revolution generatrix of the outer cylindrical surface or the outer conical surface of the annular ring is a straight line or an approximate straight line, the absolute value of the included angle between the revolution generatrix and the axis of the conical disc is less than 5 °, the width of the annular ring in the direction of the axis of the conical disc is Tc, the Tc is the distance from the intersection point of the generatrix of the conical disc of the annular ring conical disc and the generatrix of the annular ring to the axis of the conical disc at the outer edge of the other end of the annular ring in the direction of the axis of the annular ring conical disc, and the Tc satisfies Tc > (D11+ D12+ D21+ D22)/160.
Preferably, the cone disc pressurizing device comprises a disc spring or a disc spring group and an end cam group formed by at least one pair of end cams, the disc spring group and the end cam are coaxially arranged with the axis of the cone disc, and the cone disc pressurizing device is arranged on one side of a driving movable cone disc and/or one side of a driven movable cone disc in the axial direction.
One end of the disc spring group is connected with one end face cam in the end face cam group, and the other end face cam is directly or indirectly connected with the driving cone disc shaft through an end face bearing.
Or one end of the disc spring group is connected with one end face cam in the end face cam group, and the other end face cam is directly connected with the driving cone disc shaft; the other end of the disc spring group is connected with the driving cone disc through an end face bearing.
Or one end of the disc spring group is connected with one end face cam in the end face cam group, and the other end face cam is directly connected with the driving conical disc shaft.
Or, alternatively, the cone disc pressurizing means does not comprise a set of end face cams.
Preferably, the end face cam group in the conical disc pressing device comprises at least one pair of end face cams, wherein n1 roller paths distributed along the circumferential direction are respectively arranged on the opposite end faces of the end face cams, wherein n1 is more than or equal to 2; a steel ball is clamped between each group of corresponding raceways of the driving cam and the driven cam, and the diameter d of the steel ball satisfies the following conditions:
d≥0.016×(D11+D12+D21+D22)。
preferably, the speed adjusting device comprises at least one pair of disk-shaped end cams and a speed adjusting gear shaft which are arranged axially oppositely, n2 raceways which are distributed along the circumferential direction are arranged on the end face of each disk-shaped end cam (which can be uniformly distributed or non-uniformly distributed, preferably uniformly distributed), the paired raceways of the disk-shaped end cams are respectively arranged oppositely and are connected through steel balls clamped between the raceways which are arranged oppositely; one disc-shaped end cam in the speed adjusting device is connected with the driving movable conical disc and/or the driven movable conical disc through a bearing, and the other disc-shaped end cam is indirectly connected with the driving fixed conical disc and/or the driven fixed conical disc through the bearing; wherein n2 is more than or equal to 2.
Each disc-shaped end face cam is fixedly connected with 1 gear, the speed regulating gear shaft is fixedly connected with 2 other gears, and the 2 gears fixedly connected to the speed regulating gear shaft are respectively meshed with the 2 gears fixedly connected to the 2 disc-shaped end face cams to form 2 pairs of gear meshing pairs.
The reduction ratio of one pair of gear pairs close to the movable cone disc is i1, the reduction ratio of the other pair of gear pairs is i2, and i1 is not equal to i 2.
A power machine comprising a power source which is an internal combustion engine and/or an electric motor, and a continuously variable transmission device according to any one of claims 1 to 5;
the power output end of the power source is connected with the driving cone disc shaft of the stepless speed change device through a torsional vibration damper; the driven cone shaft is directly or indirectly connected with the clutch (such as indirectly connected through a speed reducing device).
Or the power output shaft of the power source is connected with the driving cone group through a clutch with a torsional vibration damping function.
Preferably, the clutch is a wet multiplate clutch provided with an actuator actuated by a motor.
The clutch comprises a driving disc, a driven disc, a friction plate set, a steel plate set, a clutch spring, a clutch pressure plate, a clutch motor, a clutch speed reducer and a clutch separation cam set; the friction plate set and the steel sheet set are respectively meshed with the clutch driving disc and the clutch driven disc in a key or spline mode, the friction plates and the steel sheets are alternately arranged to form a plurality of friction pairs, and the friction pairs are pressed tightly through the clutch spring and the clutch pressure plate.
The clutch separation cam group comprises a clutch driving cam and a clutch driven cam; the clutch motor drives the clutch driving cam and the clutch driven cam to rotate relatively through a clutch speed reducing device (such as a gear pair, a chain wheel pair, a worm gear, a planet wheel, a cam and the like); the clutch driving cam and the clutch driven cam are respectively provided with cam grooves which are oppositely arranged, balls are arranged between the clutch driving cam and the cam grooves driven by the clutch, the clutch driving cam and the clutch driving disc are directly or indirectly connected in a mode that the axial distance is unchanged (such as connection through a shaft shoulder, a check ring, a nut and the like), and the clutch driven cam is directly or indirectly connected with the clutch pressure plate (such as connection through a bearing, a pull rod and the like).
Preferably, the clutch is a centrifugal clutch; the clutch comprises a driving disk, a driven disk, a centrifugal element, a friction element and a reset element;
the driving disk is connected with the centrifugal element for transferring rotation from the driving disk to the centrifugal element.
Above a set rotational speed threshold, the centrifugal element is set into axial movement by centrifugal force, thereby driving the friction element into contact with the driven disk.
Below a set rotational speed threshold, the reset element drives the centrifugal element and the friction element out of contact with the driven disc.
Preferably, the clutch is a combination of a wet plate clutch and a centrifugal clutch, and the clutch is provided with an actuator driven by a motor.
The clutch comprises a driving disc, a driven disc, a friction plate set, a steel plate set, a clutch spring, a clutch pressure plate, a clutch motor, a clutch speed reducer and a clutch separation cam set; the friction plate set and the steel sheet set are respectively meshed with the clutch driving disc and the clutch driven disc in a key or spline mode, the friction plates and the steel sheets are alternately arranged to form a plurality of friction pairs, and the friction pairs are pressed tightly through the clutch spring and the clutch pressure plate.
The clutch is characterized in that a limiter is installed at one end of the driven plate, a centrifugal roller is arranged in the limiter and is installed in the limiter through a swing rod in a contact mode, the centrifugal roller is in contact with the clutch pressure plate, a disc spring is arranged between the limiter and the driven plate, the clutch separation cam set comprises a separation cam and a fixed cam, a clutch motor is meshed with the separation cam through a clutch speed reducer, a transmission part is arranged between the separation cam and the fixed cam, the transmission part can enable the separation cam to axially move when the separation cam and the fixed cam rotate relatively, the separation cam is fixedly connected with a clutch pull rod, the clutch pull rod is installed with a pull ring through a bearing, and one end of the pull ring is in contact with the limiter.
Preferably, a bi-directional overrunning clutch is provided between the driven cone set and the final external load (e.g., a tire of a vehicle). Power can be transmitted from the continuously variable transmission and the power source side to the external load side, but cannot be transmitted from the external load side to the power source and the continuously variable transmission side.
The torsion damper or the clutch with the torsion damping function is provided with at least 1 spring with circumferential compression direction, the distance from the center of the spring to the center of the clutch is Rcs1, the stiffness coefficient of the spring is k1, and at least one spring in the springs meets the following requirements: k1 × Rcs1< 4500N.
The invention has the following effects:
1. because in the disc spring pressurization scheme, the pressurization force is not adjusted along with the change of the external load, but is always kept at a higher level, the invention ensures the reliability of the chain and the system by improving the structure, the definition and the combination of materials of the chain.
2. The annular ring is arranged on the outer edge of the conical disc, so that on one hand, the rigidity of the conical disc is increased on the premise of not influencing the main structure and size, the reduction of the thickness of the conical disc and the weight of a system is facilitated, on the other hand, the difficulty of assembly and maintenance can be effectively reduced, the manufacturing cost is indirectly reduced, the assembly precision is improved, and in addition, the annular ring is also beneficial to dynamic distribution of lubricating oil and is beneficial to lubrication and cooling.
3. The invention integrates cam pressurization on the basis of disc spring pressurization, can dynamically adjust the pressurization pressure according to external load, and effectively improves the transmission efficiency of the system, the service life of the system and the reliability of the system.
4. The invention ensures the reliability of the pressurizing system by defining the number of the steel balls in the pressurizing cam and the diameter of the steel balls.
5. The power machine of the invention ensures the robustness of the system under the extreme working conditions of sudden braking and the like by setting the torsional vibration damper and the position of the clutch system, and reduces and avoids the interference of factors such as the vibration of an internal combustion engine and the like to the friction transmission.
6. The invention provides an electromechanical control wet clutch suitable for small power machinery, which achieves the purposes of overall miniaturization and light weight by reasonably arranging components such as a motor, an actuating mechanism and the like.
7. The power machine integrates the advantages of the electric control wet clutch and the centrifugal clutch through the reasonable arrangement of all subsystems and the matching of the electric control wet clutch and the stepless speed changer.
8. According to the invention, the bidirectional overrunning clutch is arranged between the continuously variable transmission and the final load, so that power can be transmitted to the wheel end from the power source but cannot be transmitted to the power source end from the wheel end, the operation of a driver is facilitated, the sliding resistance is reduced, the external load impact is avoided, the driving comfort is improved, and the service life of the system is prolonged.
9. The torsional damper is specifically arranged, so that the capability of the system for dealing with impact load is improved, the reliability of the system is improved, and the service life of the system is prolonged.
Drawings
Fig. 1 is a schematic structural view of a continuously variable transmission of embodiment 1 of the invention.
Fig. 2 is a schematic structural diagram of an arrangement mode of a pressurizing device in embodiment 2 of the present invention.
Fig. 3 is a schematic structural diagram of an arrangement mode of a pressurizing device in embodiment 3 of the present invention.
Fig. 4 is a schematic structural view of a continuously variable transmission of embodiment 4 of the invention.
Fig. 5 is a schematic structural view of a continuously variable transmission of embodiment 5 of the invention.
Fig. 6 is a schematic view showing the structure of the wet multiplate clutch in comparative example 6.
Fig. 7 is a schematic structural view of a wet multi-plate centrifugal clutch according to embodiment 6.
Fig. 8 is a schematic view showing the structure of the centrifugal clutch in comparative example 7.
Fig. 9 is a schematic structural view of a power assembly of the continuously variable transmission applied to a two-wheeled motorcycle, a three-wheeled motorcycle and an all-terrain vehicle.
FIG. 10 is a schematic structural view of a continuously variable steel belt according to the present invention.
Wherein, 1, a bearing I; 2, bearing II; 3, actively fixing a cone disc; 4 steel flexible transmission element; 5, driving the cone disc; 6, a disc spring component; 7, a first end face cam; 8, steel balls; 9 end surface cam II; 10 bearing III; 11, driving cone disc shaft; 12 bearing IV; 13 driven cone pulley shaft; 14 driven fixed cone disc; 15 driven dynamic conical disks; 16 bearing V; 17 a speed regulating shaft; 18 bearing VI; 19 a first disc-shaped end cam; 20 a bull gear I; 21, a first speed regulating gear; 22 speed-regulating steel balls; 23 a second disc-shaped end face cam; 24 gear wheels II; 25, a second speed regulating gear; 26 bearing VII; 27 bearing; 28 bearing VIII; 29 a clutch; 30 bidirectional overrunning clutch; 31 a power source; 501 an input shaft; 502 an input shaft bearing; 503 a primary gear; 504 pin shafts; 505 clutch driven disc; 506 clutch driving discs; 507 friction steel sheets; 508 friction disk; 509 a clutch pressure plate; 510 a clutch spring; 511 a bolt; a 512 clutch motor; 513 bearing IX; 514 a reduction gear; 515 bearing X; 516 oil seal; 517 a sensor seat; 518 a sensor bolt; 519 a clutch position sensor; 520 a clutch lever; 521 pull rod nuts; 522 bearing XI; 523 a separation cam; 524 fixing the cam; 525 positioning pins; 526 a housing; 527 buffer springs; 528 a clutch nut; 550 clutch driving discs; 551 clutch pressure plate; 552 a clutch housing; 553 disc springs; 554 a pull ring; 555 limit device; 556 oscillating bar; 557 centrifugal roller; 558 bearing seats; 559 bearing XII; 581 clutch flail block; 582 a clutch drum; the engine comprises a 901 engine, a 902 clutch, a 903 continuously variable transmission, a 904 clutch motor, a 905 speed regulation motor, 1001 thrust plates and 1002 steel rings.
Detailed Description
Example 1
The continuously variable transmission comprises a driving cone disc set, a driven cone disc set, a steel flexible transmission element, a speed regulating device and a cone disc pressurizing device; the driving conical disc set comprises a driving conical disc shaft, a driving fixed conical disc and a driving movable conical disc, the driving conical disc shaft is connected with the driving fixed conical disc through a bearing II, the driving movable conical disc comprises a cone with an inner hole and a hollow cylinder fixedly connected to the cone, and the driving movable conical disc is connected with the driving conical disc shaft through keys arranged in the inner hole of the cone and the inner hole of the hollow cylinder; a pressurizing device is arranged between the driving movable cone disc and the driving cone disc shaft, the pressurizing device comprises a disc spring or a disc spring group and at least one pair of end face cam groups, the disc spring group and the end face cam are coaxially arranged with the movable cone disc and the fixed cone disc, and the cone disc pressurizing device is arranged on one side of the movable cone disc in the axial direction.
The arrangement of the pressurizing means as shown in fig. 1: one end of the disc spring group is connected with the first end face cam, the second end face cam is directly connected with the driving conical disc shaft, the fixed conical disc is not fixedly connected with the conical disc shaft, and the fixed conical disc and the conical disc shaft are connected through a bearing II (namely, the end face bearing is connected with the radial bearing or a combined bearing thereof).
The driven conical disc set comprises a driven conical disc shaft, a driven fixed conical disc and a driven movable conical disc, the driven conical disc shaft is fixedly connected with the driven fixed conical disc, the driven movable conical disc comprises a cone with an inner hole and a hollow cylinder fixedly connected on the conical surface, and the driven movable conical disc is connected with the driven conical disc shaft through keys arranged in the inner hole of the cone and the inner hole of the hollow cylinder; a speed regulating device is arranged between the driven cone disk and the driven cone disk shaft.
The speed regulating device comprises at least one pair of disc-shaped end face cams which are axially arranged oppositely, n rolling ways which are uniformly distributed along the circumferential direction are arranged on the end face of each disc-shaped end face cam, and the rolling ways of the pair of disc-shaped end face cams are respectively arranged oppositely and are connected through steel balls clamped between the rolling ways which are arranged oppositely.
A first disc-shaped end face cam in the speed adjusting device is connected with a driven movable conical disc through a bearing VI, and a second disc-shaped end face cam is indirectly connected with a driven fixed conical disc through a bearing VII; the first large gear is fixedly connected to the first disc-shaped end face cam, the second large gear is fixedly connected to the second disc-shaped end face cam, the first speed regulating gear and the second speed regulating gear are fixedly connected to the speed regulating shaft, the first speed regulating gear is meshed with the first large gear, and the second speed regulating gear is meshed with the second large gear to form 2 pairs of gear meshing pairs; the reduction ratio of one pair of gear pairs close to the movable cone disc is i1, the reduction ratio of the other pair of gear pairs is i2, and i1 is not equal to i 2.
The outer edge of the driving movable cone disc, the driving fixed cone disc, the driven fixed cone disc and/or the driven movable cone disc is/are provided with an annular ring coaxial with the cone disc, a rotation bus of an outer cylinder or an outer conical surface of the annular ring is a straight line, an absolute value of an included angle between the rotation bus and the axis of the cone disc meets the condition that the included angle is smaller than 5 degrees, specifically 0 degree, and the width Tc of the annular ring along the axis of the cone disc, namely the distance from the intersection point of the bus of the cone disc and the bus of the annular ring to the outer edge of the other end of the annular ring along the axis of the cone disc, meets Tc > (D11+ D12+ D21+ D22)/160, specifically 10).
The steel flexible transmission element is clamped between the driving cone disc set and the driven cone disc set at the same time, and power and motion are transmitted between the driving cone disc set and the driven cone disc set.
The steel flexible transmission element is a swing pin chain; the oscillating pin chain consists of a plurality of chain links; 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 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 embodiment adopts two ends provided with stop pins.
The pin shaft is made of steel, and the material components comprise 0.93 wt% of C and 1.46 wt% of Cr; the chain plate is made of steel, and the material components comprise 0.67 wt% of C, 1.11 wt% of Mn, 0.70 wt% of Cr and 0.62 wt% of Ni; the stop pin is made of steel, and the C in the material composition is 0.32 wt%.
The maximum outer diameter D11 of the driving dynamic cone disc, the maximum outer diameter D12 of the driving fixed cone disc, the maximum outer diameter D21 of the driven dynamic cone disc and the maximum outer diameter D22 of the driven fixed cone disc;
the maximum width of the steel flexible transmission element in the axis direction of the conical disc is B, and the requirements are that: (D11+ D12+ D21+ D22)/12 is more than or equal to B which is more than or equal to (D11+ D12+ D21+ D22)/60. The embodiment is as follows: 30 in the axial direction of the conical disc, the projected area of the stop pin on the section perpendicular to the thickness direction of the chain plate for at least 60 percent of the length satisfies the formula: greater than or equal to (D11+ D12+ D21+ D22) ^2/1.5E 6. The embodiment is as follows: 0.24. the highest efficiency of the embodiment reaches 95%, and the speed-regulating equivalent electric power only needs 60W.
Example 2
As shown in fig. 2, the pressing device of the present embodiment is arranged in the following manner: one end of the disc spring group is connected with the first end face cam, and the second end face cam is directly connected with the driving cone disc shaft; the other end of the disc spring group is connected with the movable cone disc through a bearing II (an end face bearing); the other arrangement is the same as in example 1.
Example 3
As shown in fig. 3, the pressing device of the present embodiment is arranged in the following manner: one end of the disc spring group is connected with the first end face cam, and the second end face cam is directly or indirectly connected with the driving cone disc shaft through a bearing II.
Comparative example 1
The other setup was the same as example 1, except that the pressurizing assembly was provided with only a disc spring and no cam for pressurizing, and the comparison results were: the highest efficiency of the comparison example is 92%, the speed regulation equivalent power consumption is 100W, and simultaneously, as the forces of the disc springs are the same under the same transmission ratio and any input torque, the smaller the torque is, the larger the axial force exceeds the requirement, and the service life of the chain is reduced; and embodiment 1 because the cam can be according to the automatic adjustment axial force of input torque, consequently the whole life-span of machine is promoted.
Comparative example 2
The other settings are the same as those in embodiment 1, and the differences are that the chain material or parameters are different, specifically: the pin shaft is made of steel, and the material components comprise 0.2 wt% of C and 0.84 wt% of Cr; the chain plate is made of steel, and the material components comprise 0.26 wt% of C, 1.51 wt% of Mn, 0.25 wt% of Cr and 0.13 wt% of Ni; the stop pin is made of steel, and the C in the material composition is 0.83 wt%. The maximum width B of the steel flexible transmission element of the present comparative example in the direction of the axis of the conical disk was 60, and the area of the projection of at least 60% of the length of the stopper pin on the cross section perpendicular to the thickness direction of the link plate was specifically 0.11. The fatigue strength of this comparative example was 35% of that of example 1 by the strengthening fatigue strength test under the same conditions.
Comparative example 3
The other arrangement modes are the same as those of the embodiment 1, except that a circular ring is not arranged on the extension of the conical disc, so that the assembly difficulty is increased, the assembly efficiency is reduced by 50%, and the manufacturing cost is increased by 5%.
Example 4
As shown in fig. 4, the present embodiment is a power machine to which the transmission of embodiment 1 is applied, and is connected to an engine through a clutch with a torsional vibration damping function as a power train; the torsional vibration of the clutch is reduced by at least 1 spring, the center of the spring is located at the radius Rcs1 of the clutch, the coefficient of stiffness of the spring is k1, k1 × Rcs1<4500N is satisfied, and the coefficient is 4356N in the embodiment.
Comparative example 4
The other setup was the same as example 4 except that formula k1 xrcs 1<4500N was not satisfied, and this comparative example was 6000N, resulting in a reduction in the filtering effect of the uneven rotation of the engine, resulting in a reduction in the life of the transmission by 20% and an increase in noise by 20 db.
Example 5
As shown in fig. 5, the present embodiment is otherwise identical to embodiment 4, except that a bi-directional overrunning clutch is provided between the driven cone set and the final external load.
Comparative example 5
The other settings are the same as embodiment 5, except that no bidirectional overrunning clutch is arranged between the driven cone pulley set and the final external load, so that the sliding resistance of the whole vehicle is increased by 80%, the driving feeling is poor, the wheel impact is completely impacted on the transmission element of the transmission, and the service life of the whole vehicle is reduced by 10%.
Example 6
Other arrangements of this embodiment are the same as those of embodiment 5, except that the clutch shown in fig. 7 adopts an electrically controlled wet multi-plate and centrifugal combined clutch, the clutch driven plate is connected with the power source through a torsion plate, a friction steel plate is axially and fixedly arranged in the clutch driven plate, friction plates are circumferentially and fixedly arranged on a clutch pressure plate, the friction plates and the friction surfaces of the friction steel plate are contacted to form a friction pair, and the friction pair is pressed by a clutch spring and the clutch pressure plate. And a limiter is arranged at one end of the clutch driven disc, a centrifugal roller is arranged in the limiter, and the centrifugal roller is installed in the limiter through the contact of the swing rod. The centrifugal roller is in contact with the clutch pressure plate. And a disc spring is arranged between the limiter and the clutch driven disc. The separation combination of clutch is through clutch motor drive, and the clutch motor passes through reduction gear and separation cam meshing, but separation cam axial displacement's structure when setting up both relative rotations between separation cam and the fixed cam, separation cam and clutch pull rod fixed connection, and the pull ring is installed through the bearing to the clutch pull rod, the one end of pull ring with stopper contact. In the two controls of electric control and centrifugation, when any one function fails, the function of the clutch can be completely operated by the other control, so that the reliability and the safety are improved.
Comparative example 6
The other settings are the same as those in embodiment 6, except that as shown in fig. 6, the clutch adopts a wet multi-plate type, and a centrifugal mechanism is not arranged, so that when the electric control function fails, the clutch cannot work, the whole vehicle cannot run at all, and the reliability and the safety are reduced.
Comparative example 7
The other arrangements are the same as those of embodiment 6 except that, as shown in fig. 8, the clutch is a centrifugal clutch, and there is no electric control device, and since the combination of the centrifugal clutch is only related to the engine speed, the transmission capacity of the clutch is reduced at low speed, resulting in deterioration of the power performance.
Example 7
As shown in fig. 9, the power assembly applied to a two-wheeled motorcycle, a three-wheeled motorcycle and an all-terrain vehicle comprises an engine, a clutch and the continuously variable transmission in embodiment 1, wherein the output end of the engine is provided with an electrically controlled wet multi-plate clutch or an electrically controlled wet multi-plate and centrifugal combined clutch, the output end of the clutch is provided with the continuously variable transmission in embodiment 1, the power of the engine is transmitted to the continuously variable transmission through the clutch, and the power of the continuously variable transmission is output from a driven conical disc set and is directly or indirectly transmitted to wheels. The disengaging and engaging functions of the clutch are directly driven by the motor or indirectly driven by the speed reducing mechanism.
Example 8
In this example, the continuously variable steel belt was used in place of the pivot pin chain in example 1, and the other arrangement was the same as in example 1. As shown in fig. 10, the continuously variable steel belt comprises a plurality of thrust plates and a belt ring set, each thrust plate comprises at least one open slot for accommodating the belt ring set; the belt ring group forms a closed loop by the plurality of thrust plates in the open slot to form a steel flexible transmission element.
The set of rings is made up of a plurality of closed steel rings, each having a thickness of 0.08mm (which may be, for example, 0.07mm, 0.09mm, 0.10mm, 0.11mm, 0.12mm, 0.13mm, 0.145mm, 0.15mm, 0.16mm, 0.17mm, 0.18mm, 0.19mm, etc. in other embodiments).
The steel ring is made of maraging steel, and the maraging steel comprises the following chemical components: the carbon content is less than 0.05 wt% (e.g., 0.015 wt% for this example).
The thrust piece comprises the following chemical components: the content of carbon is 0.8-0.9 wt% (e.g., 0.82 wt% in this embodiment), the content of manganese is 0.4-0.6 wt% (e.g., 0.51 wt% in this embodiment), the content of sulfur is less than or equal to 0.03 wt% (e.g., 0.01 wt% in this embodiment), the content of phosphorus is less than or equal to 0.035 wt% (e.g., 0.008 wt% in this embodiment), the content of chromium is less than or equal to 0.25 wt% (e.g., 0.12 wt% in this embodiment), and the content of nickel is less than or equal to 0.20 wt% (e.g., about 0.01 wt% in this embodiment).

Claims (10)

1. A stepless speed change device comprises a driving cone disc set, a driven cone disc set, a steel flexible transmission element, a speed regulating device and a cone disc pressurizing device;
the driving cone disc set comprises a driving cone disc shaft, a driving fixed cone disc and a driving movable cone disc, the driving cone disc shaft is fixedly connected with the driving fixed cone disc or is connected in a mode that the driving cone disc shaft cannot rotate and cannot axially move (such as a key, an end face key, a spline, a combined nut, a check ring, a shaft shoulder and the like), the driving movable cone disc comprises a cone body with an inner hole and a hollow revolving body fixedly connected on the cone body, and the driving movable cone disc is connected with the driving cone disc shaft through the key or the spline arranged in the inner hole of the cone body and the inner hole of the hollow revolving body; a disc spring or a disc spring group is arranged between the driving cone disc and the driving cone disc shaft, and the disc spring group consists of 2 or more than 2 disc springs;
the driven conical disc set comprises a driven conical disc shaft, a driven fixed conical disc and a driven movable conical disc, the driven conical disc shaft is fixedly connected with the driven fixed conical disc or is connected in a mode that the driven conical disc shaft cannot rotate and cannot axially move (such as a key, an end face key, a spline, a combined nut, a check ring, a shaft shoulder and the like), the driven movable conical disc comprises a cone with an inner hole and a hollow revolving body fixedly connected on the cone, and the driven movable conical disc is connected with the driven conical disc shaft through the key arranged in the inner hole of the cone and the inner hole of the hollow revolving body; a speed regulating device is arranged between the driven movable conical disk and the driven conical disk shaft;
the steel flexible transmission element is clamped between the driving fixed cone disc and the driving movable cone disc and between the driven fixed cone disc and the driven movable cone disc at the same time, and is used for transmitting power and motion between the driving cone disc set and the driven cone disc set;
the maximum outer diameter of the driving movable cone disc is D11, the maximum outer diameter of the driving fixed cone disc is D12, the maximum outer diameter of the driven movable cone disc is D21, and the maximum outer diameter of the driven fixed cone disc is D22;
it is characterized in that the preparation method is characterized in that,
the steel flexible transmission element is a swing pin chain; the oscillating pin chain consists of a plurality of chain links; 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 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 which is used for limiting the chain plate to fall off from the swing pin;
the material of the pin shaft is steel, and in the chemical components of the pin shaft, the content of C is 0.8-1.2 wt%, and the content of Cr is 1.2-1.8 wt%;
the chain plate is made of steel, and in the chemical components of the chain plate, the content of C is 0.5-0.8 wt%, the content of Mn is 0.6-1.2 wt%, the content of Cr is 0.5-0.8 wt%, and the content of Ni is 0.3-0.8 wt%;
the stop pin is made of steel, and the chemical components of the stop pin comprise 0.05-0.4 wt% of C;
the maximum width of the steel flexible transmission element in the direction of the axis of the driving cone disc shaft is B, and the maximum width satisfies the following conditions:
(D11+D12+D21+D22)/12≥B≥(D11+D12+D21+D22)/60；
the length of the stop pin in the direction of the axis of the driving cone shaft is at least 60%, and the area of the projection on the section perpendicular to the thickness direction of the chain plate is more than or equal to (D11+ D12+ D21+ D22) 2 /1.5E6；
Or the steel flexible transmission element is a stepless speed change steel belt, the stepless speed change steel belt comprises a plurality of thrust pieces and a belt ring group, each thrust piece comprises at least one open slot, and the open slots are used for accommodating the belt ring group; the belt ring group forms a closed loop by the plurality of thrust plates in the open slot to form a steel flexible transmission element;
the belt ring group consists of a plurality of closed steel rings, and the thickness of each steel ring is 0.07-0.2 mm;
the steel ring is made of maraging steel, and the maraging steel comprises the following chemical components: the content of carbon is less than 0.05 wt%;
the thrust piece comprises the following chemical components: the carbon content is 0.8-0.9 wt%, the manganese content is 0.4-0.6 wt%, the sulfur content is less than or equal to 0.03 wt%, the phosphorus content is less than or equal to 0.035 wt%, the chromium content is less than or equal to 0.25 wt%, and the nickel content is less than or equal to 0.20 wt%.
2. The continuously variable transmission device according to claim 1, characterized in that:
the outer edge of one or more of the driving movable conical disc, the driving fixed conical disc, the driven movable conical disc and the driven fixed conical disc is provided with an annular ring, the conical disc provided with the annular ring is defined as an annular ring conical disc, the axis of the annular ring is coincident with the axis of the annular ring conical disc, the rotation generatrix of the outer cylindrical surface or the outer conical surface of the annular ring is a straight line or an approximate straight line, the absolute value of the included angle between the rotation generatrix and the axis of the conical disc is less than 5 degrees, the width of the annular ring in the axial direction of the annular ring conical disc is Tc, the Tc is the distance from the intersection point of the conical disc generatrix of the annular ring conical disc and the annular ring generatrix to the outer edge of the other end of the annular ring in the axial direction of the annular ring conical disc, and the Tc meets Tc (D11+ D12+ D21+ D22)/160.
3. The continuously variable transmission device according to claim 1, characterized in that:
the cone disc pressurizing device comprises a disc spring or a disc spring group and an end face cam group formed by at least one pair of end face cams, the disc spring group and the end face cams are coaxially arranged with the axis of the cone disc, and the cone disc pressurizing device is arranged on one side of a driving movable cone disc and/or one side of a driven movable cone disc in the axial direction;
one end of the disc spring group is connected with one end face cam in the end face cam group, and the other end face cam is directly or indirectly connected with the driving cone disc shaft and/or the driven cone disc shaft through a bearing;
or one end of the disc spring group is connected with one end face cam in the end face cam group, and the other end face cam is directly connected with the driving cone disc shaft and/or the driven cone disc; the other end of the disc spring group is connected with the driving dynamic cone disc and/or the driven dynamic cone disc through a bearing;
or one end of the disc spring group is connected with one end face cam in the end face cam group, the other end face cam is directly connected with the driving conical disc shaft and/or the driven conical disc shaft, instead, the driving fixed conical disc is not fixedly connected with the driving conical disc shaft and/or the driven fixed conical disc is not fixedly connected with the driven conical disc shaft, and the driving fixed conical disc is connected with the driving conical disc shaft and/or the driven fixed conical disc is connected with the driven conical disc shaft through an end face bearing, a radial bearing or a combined bearing;
or, alternatively, the cone disc pressurizing means does not comprise a set of end face cams.
4. The continuously variable transmission device according to claim 1 or 3, characterized in that: the end face cam group in the conical disc pressing device comprises at least one pair of end face cams, wherein n1 roller paths distributed along the circumferential direction are respectively arranged on the opposite end faces of the end face cams, wherein n1 is more than or equal to 2; a steel ball is clamped between each group of corresponding raceways of the driving cam and the driven cam, and the diameter d of the steel ball satisfies the following conditions:
d≥0.016×(D11+D12+D21+D22)。
5. the continuously variable transmission device according to claim 1, characterized in that: the speed regulating device comprises at least one pair of disc-shaped end cams and a speed regulating gear shaft which are axially arranged oppositely, wherein n2 roller paths distributed along the circumferential direction are arranged on the end surface of each disc-shaped end cam, and the paired roller paths of the disc-shaped end cams are respectively arranged oppositely and are connected through steel balls clamped between the roller paths arranged oppositely; one disc-shaped end cam in the speed adjusting device is connected with the driving movable conical disc and/or the driven movable conical disc through a bearing, and the other disc-shaped end cam is indirectly connected with the driving fixed conical disc and/or the driven fixed conical disc through the bearing; wherein n2 is more than or equal to 2;
each disc-shaped end face cam is fixedly connected with 1 gear, the speed regulating gear shaft is fixedly connected with another 2 gears, and the 2 gears fixedly connected with the speed regulating gear shaft are respectively meshed with the 2 gears fixedly connected with the 2 disc-shaped end face cams to form 2 pairs of gear meshing pairs;
the reduction ratio of one pair of gear pairs close to the movable cone disc is i1, the reduction ratio of the other pair of gear pairs is i2, and i1 is not equal to i 2.
6. A power machine characterized by comprising a power source which is an internal combustion engine and/or an electric motor, and a continuously variable transmission device according to any one of claims 1 to 5;
the power output end of the power source is connected with the driving cone disc shaft of the stepless speed change device through a torsional vibration damper; the driven cone disc shaft is directly or indirectly connected with the clutch (such as indirectly connected through a speed reducing device);
or the power output shaft of the power source is connected with the driving cone disc set through a clutch with a torsional vibration damping function.
7. Power machine according to claim 6, characterised in that the clutch is a wet multiplate clutch provided with an actuator driven by an electric motor;
the clutch comprises a driving disc, a driven disc, a friction plate set, a steel plate set, a clutch spring, a clutch pressure plate, a clutch motor, a clutch speed reducer and a clutch separation cam set; the friction plate set and the steel sheet set are respectively meshed with the clutch driving disc and the clutch driven disc in a key or spline mode, the friction plates and the steel sheets are alternately installed to form a plurality of friction pairs, and the friction pairs are pressed tightly through a clutch spring and a clutch pressure plate;
the clutch release cam set comprises a clutch driving cam and a clutch driven cam; the clutch motor drives the clutch driving cam and the clutch driven cam to rotate relatively through a clutch speed reducing device (such as a gear pair, a chain wheel pair, a worm gear, a planet wheel, a cam and the like); the clutch driving cam and the clutch driven cam are respectively provided with cam grooves which are oppositely arranged, balls are arranged between the clutch driving cam and the cam grooves driven by the clutch, the clutch driving cam and the clutch driving disc are directly or indirectly connected in a mode that the axial distance is unchanged (such as connection through a shaft shoulder, a check ring, a nut and the like), and the clutch driven cam is directly or indirectly connected with the clutch pressure plate (such as connection through a bearing, a pull rod and the like).
8. The power machine of claim 6, wherein the clutch is a centrifugal clutch; the clutch comprises a driving disc, a driven disc, a centrifugal element, a friction element and a reset element;
the driving disk is connected with the centrifugal element and transmits rotation from the driving disk to the centrifugal element;
above a set rotational speed threshold, the centrifugal element is set into axial movement due to centrifugal force, thereby driving the friction element into contact with the driven disc,
below a set rotational speed threshold, the reset element drives the centrifugal element and the friction element out of contact with the driven disk.
9. The power machine of claim 6,
the clutch is a combination of a wet plate clutch and a centrifugal clutch, the clutch is provided with an actuating mechanism executed by a motor,
the clutch comprises a driving disc, a driven disc, a friction plate set, a steel plate set, a clutch spring, a clutch pressure plate, a clutch motor, a clutch speed reducer and a clutch separation cam set; the friction plate set and the steel sheet set are respectively meshed with a clutch driving disc and a clutch driven disc in a key or spline mode, the friction plates and the steel sheets are alternately arranged to form a plurality of friction pairs, and the friction pairs are pressed tightly through a clutch spring and a clutch pressure plate;
the clutch is characterized in that a limiter is installed at one end of the driven plate, a centrifugal roller is arranged in the limiter and is installed in the limiter through a swing rod in a contact mode, the centrifugal roller is in contact with the clutch pressure plate, a disc spring is arranged between the limiter and the driven plate, the clutch separation cam set comprises a separation cam and a fixed cam, a clutch motor is meshed with the separation cam through a clutch speed reducer, a transmission part is arranged between the separation cam and the fixed cam, the transmission part can enable the separation cam to axially move when the separation cam and the fixed cam rotate relatively, the separation cam is fixedly connected with a clutch pull rod, the clutch pull rod is installed with a pull ring through a bearing, and one end of the pull ring is in contact with the limiter.
10. The power machine of claim 6, wherein a bi-directional overrunning clutch is provided between the driven cone pulley set and the final external load (e.g., a tire of a vehicle), power being transferable from the continuously variable transmission and power source side to the external load side and not from the external load side to the power source and continuously variable transmission side;
at least 1 spring with the circumferential compression direction is arranged on the torsional damper or on the clutch with the torsional damping function, the distance between the center of the spring and the center of the clutch is Rcs1, and the coefficient of stiffness of the spring is k 1; at least one of the springs satisfies: k1 × Rcs1< 4500N.
CN202210503125.0A 2022-05-10 2022-05-10 Stepless speed change device and power machine Active CN114838098B (en)

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Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102478105A (en) * 2010-11-24 2012-05-30 程乃士 Intelligent pressuring continuously-variable transmission
CN103867678A (en) * 2014-03-20 2014-06-18 程乃士 Cone plate type stepless speed changer
CN110762174A (en) * 2018-07-25 2020-02-07 杭州肇鹏科技有限公司 Cam-pressurized conical disc type continuously variable transmission
CN110985625A (en) * 2019-12-30 2020-04-10 杭州肇鹏科技有限公司 Stepless speed change device with built-in speed regulation component
CN111486206A (en) * 2020-04-20 2020-08-04 杭州肇鹏科技有限公司 Pendulum pin chain bearing large torque and impact load and non-road mobile machine
CN113653781A (en) * 2020-12-28 2021-11-16 重庆宗申无级变速传动有限公司 Stepless speed variator

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102478105A (en) * 2010-11-24 2012-05-30 程乃士 Intelligent pressuring continuously-variable transmission
CN103867678A (en) * 2014-03-20 2014-06-18 程乃士 Cone plate type stepless speed changer
CN110762174A (en) * 2018-07-25 2020-02-07 杭州肇鹏科技有限公司 Cam-pressurized conical disc type continuously variable transmission
CN110985625A (en) * 2019-12-30 2020-04-10 杭州肇鹏科技有限公司 Stepless speed change device with built-in speed regulation component
CN111486206A (en) * 2020-04-20 2020-08-04 杭州肇鹏科技有限公司 Pendulum pin chain bearing large torque and impact load and non-road mobile machine
CN113653781A (en) * 2020-12-28 2021-11-16 重庆宗申无级变速传动有限公司 Stepless speed variator

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