CN1511237A - Traction continuously variable transmission device, split-power transmission system and apparatus using same - Google Patents

Traction continuously variable transmission device, split-power transmission system and apparatus using same Download PDF

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Publication number
CN1511237A
CN1511237A CNA028106865A CN02810686A CN1511237A CN 1511237 A CN1511237 A CN 1511237A CN A028106865 A CNA028106865 A CN A028106865A CN 02810686 A CN02810686 A CN 02810686A CN 1511237 A CN1511237 A CN 1511237A
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China
Prior art keywords
spherical surface
rotor
counter
driven
rotating
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CNA028106865A
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Chinese (zh)
Inventor
朴鲁吉
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Individual
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Individual
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Priority claimed from KR1020010029266A external-priority patent/KR20020090270A/en
Priority claimed from KR10-2001-0041222A external-priority patent/KR100422320B1/en
Priority claimed from KR10-2002-0014976A external-priority patent/KR100426333B1/en
Application filed by Individual filed Critical Individual
Publication of CN1511237A publication Critical patent/CN1511237A/en
Pending legal-status Critical Current

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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
    • F16H15/00—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members
    • F16H15/02—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members without members having orbital motion
    • F16H15/04—Gearings providing a continuous range of gear ratios
    • F16H15/06—Gearings providing a continuous range of gear ratios in which a member A of uniform effective diameter mounted on a shaft may co-operate with different parts of a member B
    • F16H15/26—Gearings providing a continuous range of gear ratios in which a member A of uniform effective diameter mounted on a shaft may co-operate with different parts of a member B in which the member B has a spherical friction surface centered on its axis of revolution
    • 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
    • F16H15/00—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members
    • F16H15/02—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members without members having orbital motion
    • F16H15/04—Gearings providing a continuous range of gear ratios
    • F16H15/06—Gearings providing a continuous range of gear ratios in which a member A of uniform effective diameter mounted on a shaft may co-operate with different parts of a member B
    • F16H15/26—Gearings providing a continuous range of gear ratios in which a member A of uniform effective diameter mounted on a shaft may co-operate with different parts of a member B in which the member B has a spherical friction surface centered on its axis of revolution
    • F16H15/28—Gearings providing a continuous range of gear ratios in which a member A of uniform effective diameter mounted on a shaft may co-operate with different parts of a member B in which the member B has a spherical friction surface centered on its axis of revolution with external friction surface
    • 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
    • F16H15/00—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members
    • F16H15/02—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members without members having orbital motion
    • F16H15/04—Gearings providing a continuous range of gear ratios
    • F16H15/06—Gearings providing a continuous range of gear ratios in which a member A of uniform effective diameter mounted on a shaft may co-operate with different parts of a member B
    • F16H15/26—Gearings providing a continuous range of gear ratios in which a member A of uniform effective diameter mounted on a shaft may co-operate with different parts of a member B in which the member B has a spherical friction surface centered on its axis of revolution
    • F16H15/30—Gearings providing a continuous range of gear ratios in which a member A of uniform effective diameter mounted on a shaft may co-operate with different parts of a member B in which the member B has a spherical friction surface centered on its axis of revolution with internal friction surface
    • 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
    • F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
    • F16H37/06—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
    • F16H37/08—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing
    • F16H37/0833—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with arrangements for dividing torque between two or more intermediate shafts, i.e. with two or more internal power paths
    • F16H37/084—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with arrangements for dividing torque between two or more intermediate shafts, i.e. with two or more internal power paths at least one power path being a continuously variable transmission, i.e. CVT
    • 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
    • F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
    • F16H37/06—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
    • F16H37/08—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing
    • F16H37/10—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing at both ends of intermediate shafts
    • F16H2037/102—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing at both ends of intermediate shafts the input or output shaft of the transmission is connected or connectable to two or more differentials
    • 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
    • F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
    • F16H37/06—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
    • F16H37/08—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing
    • F16H37/10—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing at both ends of intermediate shafts

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Friction Gearing (AREA)

Abstract

A continuously-variable transmission device, a power split transmission system and an apparatus using either this device or system, wherein the power input to the transmission device is transmitted to a spherical rotor at an inpit side; the spherical rotor at the input side contacts with a spherical rotor configured on one end of a counter rotor assembly, and thereby rotational driving is achieved; a spherical rotor configured in the other end of a counter rotor assembly contacts with a spherical rotor at an output side and thereby rotational driving is achieved; and locations of the counter rotor assembly are adjusted by means of a quadric crank mechanism. The transmission can be configured to comprise a power split means for splitting input power into a plurality of paths, transmitting and outputting the power, using at least one planetary gear unit (PGU), and a transmission means for receiving a part of the split power from the power split means, converting its rotational force transmitting it back to the power split means, so that the power transmitted through the transmission means can be minimized to a size required for speed change.

Description

Traction continuously variable transmission, distribute power transmission and use the equipment of this device and system
Technical field
The present invention relates to a kind of traction drive constantly variable transmission, a kind of power division transmission system and use the equipment of this device and system, particularly a kind of continuous variable unit (CVU) with four pole crank mechanisms and spheroid; A kind of transmission system that is used to distribute with the device of delivering power that comprises is utilized at least one various types of planetary gear unit; A kind of transmission system, wherein continuous variable unit and power distribution unit are combined together; A kind of equipment that utilizes said apparatus and system, for example bicycle, sports equipment, automobile, toy, robot and other similar equipment.
Background technique
Usually, traditional transmission device is that speed changer (V) is divided into stepping changing cell (SVU) and continuous variable unit (CVU).Concerning SVU, there are gear mechanism and chain type mechanical structures in this.Concerning CVU, there are various traction drive mechanical structures in this, for example variable belt pulley-belt, threaded pipe, ball-dish etc.Because the SVU of gear mechanism has very high Maximum Torque, it is normally used for requiring high-power device.But the shortcoming of SVU is that velocity variations is unsmooth.Adopt the CVU of friction mechanism to have the level and smooth advantage of velocity variations, but its shortcoming is the SVU of its Maximum Torque less than gear mechanism, thereby its application is not extensive.
Usually, power division transmission system (PSTS) has following structure: the power of power source input is assigned with and to offer transmission system as much as possible little so that be transmitted to the power of speed changer.Utilize the gear connection of one or more planetary gear units (PGUs) to be called as power distribution unit.
Fig. 1, Fig. 2 show the structure of the PSTS that has utilized a PGU 10.As depicted in figs. 1 and 2, PGU 10 can be represented as the black box with three connecting element (A, B and C) usually.The I/O parts of speed changer 100 respectively with three connecting element of PGU 10 in two be connected.Power source 1 is connected with two connecting element of PGU 10 respectively with load 2.Divide two-way to PGU 10 and speed changer 100 by power source 1 as the power of motor or motor and similar device input, be combined into output then again load 2.Here, term " connecting element " refers to the parts that are connected to the external means as speed changer or power source.Three connecting element of the PGU 10 that traditional PS TS is used are ring gear (R), sun gear (S) and carrier (C).Usually, PGU 10 also has a small gear (P) except parts R, S and C.Small gear is not used as the parts that are connected with external means as the relay part of inner connection R, S and C.Small gear is divided into single small gear (SP) and compound small gear (CP).Use with PGU of the SP that only uses in traditional PS TS is known.
As shown in Figure 3, it also is known using the structure of the PSTS of two PGU (PGU1 and PGU2).The example that Fig. 3 (a) illustrates can be summarized as the structure shown in Fig. 3 (b).In such traditional PS TS structure, two connecting element PGU1 10 (for example are connected with port b at port a with PGU2 20, in described example, the carrier of PGU1 is connected to the sun gear of PGU2, the sun gear of PGU1 is connected to the carrier of PGU2), PGU1 10 and PGU2 20 respectively have three connecting element.Power source 1 and load 2 are connected to tie point (port a and port b).Transmission device 100 ' be connected keeps between the disconnected tie point that does not connect, promptly between the ring gear (port d) of the ring gear (port c) of PGU1 and PGU2.
The shortcoming of traditional speed changer like this is, considers from structure, and it is used for high power and has any problem.For example, friction speed variator has low Maximum Torque.According to the hertz contact theory, the size and the direction of radius according to the curved section of contact (part) can produce difference on contact pressure and elasticity tension.The tradition friction speed variator has such structure, and promptly when any two objects (spheroid, cylinder, cone or disk) when contacting with each other selectively, its Maximum Torque must be low.Traditional C VU also has the not wide shortcoming of transmission gear ratio scope.If in PSTS, use traditional CVU, can not obtain desired wide overall ratio (OSR).Therefore, concerning traditional PS TS, must be respectively provide separately clutch, so that, obtain desired OSR by adopting the multimodal method of realizing for the power distribution unit separately of each scope to low-speed range and high-speed range.Multimodal method is very complicated, thereby causes the increase of weight.
As mentioned above, the traditional PS TS that uses one or two PGU is known, wherein only uses the simple PGU with single small gear, ring gear (R), sun gear (S) and carrier (C).In such traditional PS TS, if only rely on simple PGU obtain desired OSR variation scope, it is very big that related gear size must become.Thus, the application of simple PGU is restricted.In addition, concerning the PSTS that uses two PGU, power source and load are connected to the tie point of PGU1 and PGU2, and transmission device only is connected to the connecting element that not to connect, the result who does like this be design very restricted.Therefore, the PSTS that meets the structure with variation of various rate request by the traditional PS TS design of using two PGU is unusual difficulty.
Summary of the invention
Therefore, one object of the present invention be to provide a kind of device, a kind of system and a kind of improved equipment to solve aforementioned conventional power division transmission system problem and the restriction of traditional C VU.
For reaching this purpose, another object of the present invention is to by providing traction drive CVT device to improve the Maximum Torque of speed changer, this traction drive CVT device has four pole crank mechanism and the friction wheel mechanisms that are used for the stabilized speed change operation, and the ball inner and outer surface contacts with each other in this friction wheel mechanism.
Another object of the present invention is to by the allocating power dispensing device to comprise S, S and C or R, R and C as parts, provide one or more CP to PGU then, thereby for the various designs of power division transmission system provide flexibility, wherein power distribution unit distributes the power by the power source input to be sent to transmission device with a part that only allows power.
The present invention also has a purpose to be to provide flexibility for the various designs of power division transmission system.PGU1 and PGU2 are by interconnected tie point so that power source and load are connected to two connecting element by power distribution unit is provided for this, and wherein power distribution unit distributes and comes from the input power of power source so that only allow a part of power to be sent to transmission device.
The present invention also has a purpose that the Continuously Variable Transmission system that provides a Maximum Torque and velocity variations scope significantly to increase is provided.The result is, by power division type traction drive CVT is provided system, this Continuously Variable Transmission system can be used to high power applications such as passenger vehicle or more senior application, in this power division type traction drive CVT system, the constantly variable transmission with four pole crank mechanisms and spheroid rotor combines with power distribution unit.
For achieving the above object, one aspect of the present invention provides a kind of transmission system, is used for changing continuously and transmitting the rotating force of input, and this transmission system comprises: drive rotor, at least one part on its surface has first spherical surface, and this drives the rotating force driving of rotor by input; Driven rotor, at least one part on its surface has second spherical surface, and the rotating force that comes from drive unit is accepted and transmitted to this driven rotor; Counter-rotating rotor (counter rotor) assembly, have the counter-rotating rotor of driving and driven counter-rotating rotor, be used for the rotating force between relaying driving rotor and the driven rotor, the driving counter-rotating rotor has the 3rd spherical surface in its at least one part of surface and is used for by driving the rotor traction drive, and driven counter-rotating rotor has the 4th spherical surface in its at least one part of surface and is used for by the driven rotor traction drive; Four pole crank mechanisms are equipped with rotatable counter-rotating rotor assembly, are used to adjust the position of counter-rotating rotor assembly.Four pole crank mechanisms comprise: stationary links is fixed in the framework of CVT device; Crank has first rotatable pivot that is fixed in stationary links one end and first joint that is positioned at the stationary links the other end, is used for position regulation; Rotary connector, an end are fixed in first joint of crank, and the other end has second joint; Rotatable follower is fixed on second tie point of connector, has the second rotatable pivot of the other end that is fixed in stationary links, and follower relies on the motion of crank and movable.The counter-rotating rotor assembly has coupling shaft, and this coupling shaft is used for connecting the driving counter-rotating rotor, and extremely driven counter-rotating rotor is so that rotors can be rotated together, and the structure of this coupling shaft is a hollow, and the rotary connector of four pole crank mechanisms is fixed in the quill shaft.In a preferred embodiment of the invention, first pivot of four pole crank mechanisms is positioned at the center of the spherical surface (first spherical surface) that drives rotor; Second pivot is positioned at the center of the spherical surface (second spherical surface) of driven rotor; First joint is positioned at the center of the spherical surface (the 3rd spherical surface) that drives counter-rotating rotor; Second joint is positioned at the center of the spherical surface (the 4th spherical surface) of driven counter-rotating rotor.
Another aspect of the present invention provides a kind of power division transmission system of power conversion device, be used for input Power Distribution is become two paths and transmits and export this power, this conveying system comprises: power distribution unit, comprise planetary gear unit (PGU), perhaps comprise planetary gear unit with at least one compound small gear, two ring gears and a carrier with at least one compound small gear, two sun gears and a carrier; Transmission device, it is the stepping variable drive assembly, or the CVT device, is used to accept come from the part, conversion of the distribution power of power distribution unit and rotating force power is sent back dispensing device.In this aspect of the invention, first connecting element of PGU directly or by attenuator (or amplifier) is connected to power source; Second connecting element of PGU directly or by attenuator (or amplifier) is connected to load; Transmission device directly or by attenuator (or amplifier) is connected between first connecting element of PGU and the 3rd connecting element or between the 3rd connecting element and second connecting element.
The power division conveying system that provides power conversion unit more on the one hand of the present invention, wherein this conveying system comprises: power distribution unit, have and come from the first gear link unit, the combination of two PGU that connection of second gear or the 3rd gear connect, be used for by utilizing two PGU to distribute input power to path more than one, transmit and export this power, wherein the first gear link unit has a sun gear, a ring gear, a single or compound small gear and a carrier, this second gear connection has two sun gears, at least one compound small gear and a carrier, the connection of the 3rd gear has two ring gears, at least one compound small gear and a carrier; Transmission device, it is variable transmission device or the CVT device of stepping, be used to accept to come from power distribution unit distribution power a part and its rotating force sent back power distribution unit.In this case, the combination of two PGU comprises: first connecting element is first parts of a PGU; Second connecting element is first parts of the 2nd PGU; The 3rd connecting element is made of the tie point of second parts of second parts of a PGU and the 2nd PGU; The 4th connecting element is made of the tie point of the 3rd parts of the 3rd parts of a PGU and the 2nd PGU.First connecting element directly or by attenuator (or amplifier) is connected to power source; Second connecting element directly or by attenuator (or amplifier) is connected to load; Transmission device directly or by attenuator (or amplifier) is connected between first connecting element of PGU and first tie point or between first tie point and second connecting element or between first tie point and second tie point.
The present invention also provides the transmission system of power conversion unit, and wherein this transmission system comprises: the CVT device has four pole crank mechanisms and the power distribution unit that uses one or two PGU.The present invention also provides motorcycle, automobile, industrial machine, bicycle, toy, robot or the similar products that comprised above-mentioned CVT device or transmission system.
Below, will describe the present invention in detail by each embodiment.Obviously, to one skilled in the art, following examples only are used to the present invention is described but not limit the scope of the invention.Therefore, those skilled in the art can consider simple variation and modification, and these variations and modification all belong to connotation of the present invention and scope.
Description of drawings
Of the present invention these and other feature, aspect and advantage will easier quilt be understood by following explanation, claim and accompanying drawing, in the accompanying drawing, same parts is represented with same numeral.
Fig. 1, Fig. 2 are the Block Diagram of example that comprises the power division transmission system of the planetary gear unit (PGU) with three connecting element (A, B and C);
Fig. 3 (a) and (b) show the example of the power division transmission system of the combination that comprises two conventional P GU;
The structure and the operation of the specific embodiment of the CVT device of Fig. 4 to 6 explanation four pole crank mechanisms used according to the invention and spherical spinner;
Fig. 7 to 11 shows the variant of the CVT device of four pole crank mechanisms used according to the invention and spherical spinner;
Figure 12 and 13 shows the driver element of the speed of the CVT device that is used to control four pole crank mechanisms used according to the invention and spherical spinner;
Figure 14 (a) and (b) and the example that (c) shows the PGU that has comprised compound small gear (CP);
Figure 15 to 17 shows the Block Diagram of example of the power division transmission system of the combination that comprises the PGU with two connecting element (A and B) and two tie points (C and D);
Figure 18 shows the type of the friction surface that traction drive system adopts;
Figure 19 shows the performance curve of the embodiment among Figure 14 (C).
Embodiment
Below, describe the preferred embodiments of the present invention in detail with reference to accompanying drawing.
Fig. 1 to 3 had been illustrated when describing prior art.The traction drive constantly variable transmission (CVT) of four pole crank mechanisms and spherical spinner is used in Fig. 4 to 13 explanation according to an aspect of the present invention.The following describes the traction drive CVT device that uses spherical spinner (friction wheel), one of them spherical contacts another spherical, but the invention is not restricted to this embodiment.It is to be noted, according to the present invention, can dispose the counter-rotating rotor assembly, promptly rely on the driving rotor and the driven rotor of four pole crank mechanisms, use friction wheel to replace spherical spinner, these friction wheels have various types of surface of contact, for example typical planar friction wheel, cone friction wheel, cylindrical body friction wheel etc.
Figure 4 and 5 are to be used for illustrating that one of them spherical contacts another spherical according to the structure of the traction drive CVT device of one embodiment of the present of invention and the schematic representation of mechanical relation.Fig. 6 (a) and (b) as the embodiment's of schematic view illustrating Fig. 4 operation.As shown in these figures, the preferred embodiments of the present invention are traction drive CVT devices 100, be used for transmitting continuously the rotating force of input, comprise: the driving rotor 120 that is positioned at input side, be positioned at the driven rotor 180 of outlet side, rotor played the counter-rotating rotor assembly 140 and the four pole crank mechanisms 150 that are used for the position of adjusting part 140 of relaying action.
Drive the rotating force rotation of rotor 120 by means of input.The input rotating force can be provided by motor, motor or manpower.At least a portion that drives the surface of rotor 120 is a spherical surface.Just just require spherical surface for traction drive.That is to say, needn't all be shape as shown in the drawing according to each rotor of the present invention.For example, if what use is outer spherical surface, it can be a solid sphere, if what use is the inner spherical surface, then externally is four prism type usually perhaps.The present invention only needs spherical surface at the contact area that is used for by the transmission of traction-driven power.In the zone that is not spherical surface, it can be a different shape.As for driving rotor, the variability of so many shape also is applicable to the rotor at driven rotor and counter-rotating rotor assembly two ends.Driven rotor 180 is accepted to come from the rotating force that drives rotor 120 and to export this rotating force by the counter-rotating rotor assembly, and as in the situation of driving rotor 120, at least one part that wherein should the surface is a spherical surface requiring the traction-driven zone.In the following embodiments, spherical surface can be present in inside or outside.
Counter-rotating rotor assembly 140 transmits rotating force between driving rotor 120 and driven rotor 180.Counter-rotating rotor assembly 140 has the counter-rotating rotor 142 of driving and driven counter-rotating rotor 146.Driving counter-rotating rotor 142 is by the part of friction driving by contacting with 120 rotations of driving rotor.Driven counter-rotating rotor 146 is by rotating the part of contact friction driving driven rotor 180.Driving counter-rotating rotor 142 and driven counter-rotating rotor 146 at least one part on surface separately, provide friction desired spherical surface respectively.The position of counter-rotating rotor assembly is regulated by four pole crank mechanisms 150.Like this, when the surface of surface that drives rotor, driven rotor and counter-rotating rotor assembly contacted with each other with the acquisition rotation, power also was that rotating force just is transmitted by frictional force.
With reference to Fig. 5, the mechanism of the contact segment F1 of spherical surface is described below.Because the outer spherical surface of the inner ball surface of driving rotor 120 and the driving counter-rotating rotor 142 of counter-rotating rotor assembly 140 has different radiuses, can obtain point of contact in contact segment in theory.Yet, in fact since the effect of the normal force of contact segment produced local elasticity's distortion, thereby formed circular contact area.According to Hertz theory, in this case, the distribution of contact pressure is, on the one hand, at the center the highest pressure arranged, and on the other hand, the pressure on the border is 0.According to ' action and reaction rule ', utilize the driving torque that drives rotor 120, formed tangential force in contact segment.Then, because the tangential force and the tangential velocity of contact segment, power is transmitted to the driving counter-rotating rotor of counter-rotating rotor assembly 140.In this case, if the tangential force of contact segment is within the scope of maximum static friction force (its value can multiply by friction factor by the normal force of contact segment and obtain), two absolute velocities that connect rotor (drive rotor and drive counter-rotating rotor) equate at the center of contact segment, thereby obtain to rotate.On the other hand, if tangential force greater than maximum static friction force, the absolute velocity of two rotors is just different, thereby slides, transmission has a negative impact to power conversely for this.The advantage of the preferred embodiments of the present invention is to utilize by employing the CVT device of four pole crank mechanisms and/or spherical spinner, and such slip is minimized.
In a preferred embodiment of the invention, first pivot 151 of four pole crank mechanisms 150 is positioned at the center of the spherical surface that drives rotor 120; Second pivot 157 is positioned at the center of the spherical surface of driven rotor 180; First joint 153 is positioned at the center of the spherical surface that drives counter-rotating rotor 142; Second joint 155 is positioned at the center of the spherical surface of driven counter-rotating rotor 146.In another example, as selection, first pivot 155 and first joint 153 alternately are positioned at the driven rotor place of outlet side, second pivot 157 and second joint 155 can be positioned at the driving rotor place of input side, like this, an advantage of the present invention is, if the position consistency of the position of the pivot of four pole crank mechanisms and those centre of rotor, always contact segment can keep static no matter crank position how.In this case, another advantage of the present invention is, the relative position at the radius of the curved section by regulating each spherical surface, the center of each spherical surface and each of four pole crank mechanisms are connected the length of (bar), the easier configuration of structure (this makes it possible to four pole crank motion of mechanism are controlled accurately).Because the adjusting of four pole crank motion of mechanism by the angle of swing of crank realize,, can obtain the scope of various gear ratio according to the scope of the angle of swing of crank.Can make velocity ratio maximization according to the rotating range of such crank by the shape of suitably adjusting each part.
With reference to Fig. 4, the rotating ratio ρ that drives between rotor 120 and the driven rotor 180 can determine shown in equation 1, all only rotate separately and under the skid-resistant condition at the rotor that drives rotor 120, driven rotor 180 and between rotor 120 and 180, realize traction-driven counter-rotating rotor assembly, according to the principle of traction drive velocity variations:
ρ = ω 2 ω 1 = r 2 r 1 r 3 r 4 [equation 1]
ω wherein 1Be the angular velocity that drives rotor 120; ω 2Be the angular velocity of driven rotor 180; r 1Be from point of contact F 1Perpendicular distance to the running shaft that drives rotor; r 2Be from point of contact F 1Perpendicular distance to the running shaft of the driving counter-rotating rotor of counter-rotating rotor assembly 140; r 3Be from point of contact F 2Perpendicular distance to the running shaft of the driven counter-rotating rotor of counter-rotating rotor assembly 140; r 4Be from point of contact F 2Arrive the perpendicular distance of the running shaft of driven rotor 180.According to equation 1, it is pointed out that can be by changing point of contact F 1And F 2Change velocity ratio with position with respect to the running shaft of the driving rotor 120 of the frame fixation of CVT device and driven rotor 180.Point of contact F 1And F 2The variation of position can obtain by the position that changes counter-rotating rotor assembly 140, wherein the position of the crank of the position of counter-rotating rotor assembly 140 by moving four pole crank mechanisms 150 is determined.
As shown in Figure 6, obviously, the motion of counter-rotating rotor assembly 140 is corresponding in the angle of rotation range Theta 1The motion of the crank 154 of interior motion is with adjusted position.In response to the motion of crank 154, follower 158 is also in corresponding angle of rotation range Theta 2Interior motion.In this case, although the angle of rotation scope of crank 154 is constants, the variable r in the equation 1 1, r 2, r 3And r 4Can be dependent on the shape of the spherical surface that is used for friction driving and is touched and change.Like this, speed also can be according to the r that changes than scope 1, r 2, r 3And r 4Value in required scope, be determined wide or narrowly.Therefore, the advantage that has in theory of CVT device of the present invention be the transmission scope be velocity ratio can reformed scope can be as required wide as much as possible.Fig. 6 shows the angular velocity θ of crank 1 54 and follower 158 1And θ 2Excursion be restricted to first and the situation of third quadrant respectively.In this case, as expected from equation 1, velocity ratio only have on the occasion of.On the other hand, in different structures, the excursion of the angle of rotation of crank can be at first and second quadrants (that is, at the point of contact F of driving side 1Be positioned at the left side of the running shaft that drives rotor 120), perhaps the excursion of the angle of rotation of follower can be crossed over third and fourth quadrant (that is, at the point of contact F of slave end 2Be positioned at the right of the running shaft of driven rotor).In this case, the scope of velocity ratio can from negative value change on the occasion of.Negative velocity is actual than the rotational speed that means the rotational speed that drives rotor and driven rotor to be opposite, that is, with respect to positive velocity ratio, the direction of rotation is opposite.In this case, the point of contact of crank 154 or follower 158 can lay respectively at the running shaft of driving rotor or running shaft (that is angle of rotation θ, of driven rotor 1And θ 2Be 0).If the angle of rotation θ of crank 154 1Be 0, r 1=0, velocity ratio becomes 0 so.Although this just means that driving rotor 120 is rotated, counter-rotating rotor assembly 140 and driven rotor 180 be not motion in fact.If the angle of rotation θ of follower 158 2Be 0, r 4=0, velocity ratio is infinitely great so.Although this just means that driven rotor 180 is rotated, the in fact not motion of counter-rotating rotor assembly 140 and driving rotor 180.
In this embodiment, counter-rotating rotor assembly 140 can be provided with a coupling shaft 144, to be used for that driving counter-rotating rotor 142 is connected to driven counter-rotating rotor 146 so that rotor 142 and 146 can rotate together.In this case, coupling shaft 144 can be configured to quill shaft, so that the connector 156 of rotatable four pole crank mechanisms 150 can be fixed in the quill shaft.In this embodiment, advantage is and can becomes separately by required rotor design with counter-rotating rotor assembly 140 two ends, also can be designed to compacter device.In different examples, coupling shaft 144 is other shape but not quill shaft.In this case, rotor 142 and 146 functions that can rotate together only in order to carry out two ends, axle 144 can be an Any shape.
Fig. 7 to 11 illustrative is revised the structure of the CVT device among the next various embodiments by the embodiment of Fig. 4.These embodiments can be according to the types of the contact segment of rotor and are distinguished mutually.The type of contact segment can be respectively in carrying out-outer, outer-Nei and outer-outer contacting and made, therefore can expect nine kinds of combinations.These embodiments are similar using aspect spherical spinner and the four pole crank mechanisms except the contact type difference of spherical surface, and it also is similar that similar advantage and operation are arranged.
Before this with reference to the schematic view illustrating of Fig. 4 to 6 preferred embodiment of traction drive CVT of the present invention.The type of the friction surface among this embodiment is that inner spherical surface-outer spherical surface contact contacts with outer spherical surface-inner spherical surface.In the embodiment shown in fig. 7, the spherical surface of the driving rotor 120 that contacts with driving counter-rotating rotor 142 is inner ball surface, and the spherical surface of the counter-rotating rotor assembly 140 that contacts with rotor 120 is outer spherical surfaces.On the other hand, the spherical surface of the driven counter-rotating rotor 146 of the counter-rotating rotor assembly 140 that contacts with driven rotor 180 is inner ball surface, and the spherical surface of the driven rotor 180 that contacts with driven counter-rotating rotor 146 is outer spherical surfaces.In such inner spherical surface-outer spherical surface contact structures, both contact areas all show as wide relatively circle (band).In another embodiment, both contact areas all show as wide relatively border circular areas (band), promptly, the contact of spherical surface realizes by outer-Nei and interior-outer contacting structure, can by with reference to the schematic view illustrating of Fig. 4 to 6 (inner spherical surface-outer spherical surface contact and outer spherical surface-inner spherical is surperficial contact) embodiment, embodiment shown in Figure 9 (contact of outer spherical surface-inner spherical surface contact with inner spherical surface-outer spherical surface) and other embodiment who does not illustrate (outer spherical surface-inner spherical surface contacts with outer spherical surface-inner spherical is surperficial and contacts) but not embodiment's (the inner spherical surface relevant with the order of power transmission-outer spherical surface contacts and contacts with inner spherical surface-outer spherical surface) shown in Figure 7 further represent.
Reach among the embodiment's (outer spherical surface-outer spherical surface contact contacts with outer spherical surface-inner spherical surface) who does not illustrate in the embodiment shown in Fig. 8 (inner spherical surface-outer spherical surface contact contacts with outer spherical surface-outer spherical surface), Figure 10 (outer spherical surface-outer spherical surface contact contacts with inner spherical surface-outer spherical surface), one of contact segment is outer-outer spherical surface contact, and another part is outer-Nei or interior-outer spherical surface contact.Outward-one feature is arranged is that contact area is narrow to the type of outer spherical surface contact.Therefore, these embodiments have following advantage: because so narrow contact area can be utilized with wide contact area, can design according to various moving conditions.At last, (outer-outer spherical surface contact and outer-outer spherical surface contacts) embodiment illustrated in fig. 11 be outside-the outer contacting type, it is outer spherical surface that all that wherein drive rotor 120, driving counter-rotating rotor 142, driven counter-rotating rotor 146 and driven rotor 180 contact spherical surface.Such contact type and aforementioned type similitude are less, but the feature of embodiments of the invention is that the position of counter-rotating rotor assembly is by four pole crank institutional adjustments.Compare with conventional apparatus, it is can obtain stable and accurate speed controlling that the present invention also has an advantage.
In Figure 18, the friction surface type that the inner spherical surface-outer spherical surface that obtains according to one embodiment of the present of invention contacts is compared with traditional traction drive CVT device.Figure 18 (a) indicating panel-ball contact, Figure 18 (b) expression ball-ball contact, Figure 18 (c) expression annular (toroidal) contact, Figure 18 (d) represent according to interior-outer contacting used in the preferred embodiments of the present invention.Below table 1 maximum contact pressure that depends on the radius ratio (r1/r0) of friction bowl under every kind of situation has been described, its maximum contact pressure that used in the present invention inner spherical surface-outer spherical surface friction type has been described well is little.In this table, the value of maximum contact pressure is the relative value with respect to the contact of dish-ball.Less comparatively speaking maximum contact pressure value means that corresponding conveying means has higher Maximum Torque compared with the conveying means of the dish-ball contact of same size.Relative value in the table 1 is based on the hertz contact theory, wherein maximum contact pressure be the contact object curved section radius sum reciprocal 2/3.For example, if r 1/ r 2=2.0, maximum contact pressure is 1.310 in ball-ball contact so, is 1.1 in the annular contact, is 0.630 in interior-outer contacting.In addition, it is pointed out that r 1/ r 0More little, promptly the radius ratio of friction bowl for example becomes 1.5,1.2 or the like, and this value is more little.Can be expected by aforementioned relative value: interior-outer contacting always has higher Maximum Torque compared with the dish-ball or the ball-ball contact of same size.On the contrary, with annular contact gear ratio than the time, if r 1/ r 0Greater than 2.0, relative value is still tended to littler.If r 1/ r 0Just there is not preferred embodiment greater than 3.0, yet, do not think in the annular in practice contact gear ratio-outer contacting is better.
[table 1]
????1.0 ????1.2 ????1.5 ????2.0 ????3.0 ????∞
Ball-ball ????1.587 ????1.498 ????1.406 ????1.310 ????1.211 ????1.000
Annular ????1.842 ????1.631 ????1.406 ????1.1 ????0.886 ????0.0
In-outer ????0.000 ????0.303 ????0.481 ????0.630 ????0.763 ????1.000
In having the CVT device of aforementioned structure, power source is connected with driving rotor 120, and load is connected with driven rotor 180.Can select that also this device is configured to power source and be connected with driven rotor 180, load is connected with driving rotor 120.Used the traction drive CVT device of aforementioned four pole crank mechanisms and spherical spinner independently to use, also can be included in power division, the CVT device by combining with the following power distribution unit of the present invention that will describe or traditional power distribution unit.Although aforementioned Maximum Torque according to traction drive CVT device of the present invention has had improvement with respect to traditional C VT device, the power transmission that exceeds this requirement in the passenger vehicle is restricted.But, if conveying system is configured to combine with the power distribution unit that has according to the CVT device of another aspect of the present invention, just can in being higher than the high power machines of passenger vehicle, power level use traction drive CVT device with low-power transmission capacity.
Can comprise four pole crank mechanisms or the traction drive CVT device of spherical spinner or traditional stepping variable drive assembly or CVT device according to power division transmission system of the present invention with previous constructions.Traditional C VT device can be a kind of in belt variable belt pulley type, taper draught wheel type, dish-type and the spherical surface ball-type transmission device.The stepping variable transmission can be gearing or chain apparatus.PSTS also comprises power distribution unit, and this power distribution unit preferably uses PGU (planetary gear unit).According to the present invention, included PGU comprises compound gear (CP) in the power distribution unit, carrier and two sun gears (S) or two ring gears (R).As selection, two PGU (PGU1 and PGU2) also can be connected to become a combination by two parts respectively in the power distribution unit.In this case, the PGU of power distribution unit has the connecting element that two or three power sources are supplied with the input rotating force for it; And the load that outputs at last of power; And can connect conveying means respectively.Connecting element also can be selected to be connected with power source by additional device such as attenuator or amplifier.
With reference to Figure 14, the figure shows the PGU that is used to dispose according to PSTS of the present invention.The PGU (10 ') that structure shown in Figure 14 (a) is made up of compound small gear (CP), carrier (C) and two sun gears (S).The PGU that structure shown in Figure 14 (b) is made up of compound small gear (CP), carrier (C) and two ring gears (S) (10 ").If the PGU with structure shown in Figure 14 be connected with conveying means 100 with reference to the described power source 1 of Fig. 1 and 2, load 2, the result just constitutes power division transmission system (PSTS).
With reference to Fig. 2, the equation between overall ratio (OSR) δ of the velocity ratio ρ of transmission (device) and whole drive system can be done following expression, and PGU is expressed as black box:
ρ = B δ - A [equation 2]
In variator power be than the equation between (VPR) ψ and the δ
ψ = 1 - δ A [equation 3]
Wherein A and B are according to the gear-type that is provided with for PGU and size, first, second and the definite systematic parameter of the 3rd connecting element.Figure 14 (c) shows the embodiment according to transmission system of the present invention who has the PGU shown in Figure 14 (a) and disposed structure as shown in Figure 2.In the embodiment shown in Figure 14 (c), carrier (C) is connected with power source (i); First sun gear (S1) that is connected with first small gear (P1) of compound small gear is connected with load (o); The secondary sun wheel (S2) that is connected with second small gear (P2) of compound small gear is connected with the input of CVU; First sun gear (S1) is connected with the output of CVU.
In the table 2 below, with traditional PGU with the use shown in Figure 14 (c) a embodiment according to the transmission system of PGU of the present invention compare, wherein conventional P GU comprises a sun gear, a ring gear, a carrier and a single small gear, and the PGU of the present invention among the embodiment comprises two sun gears, a carrier and a compound small gear.
[table 2]
Figure A0281068600233
In table 2, R cThe inclination radius of expression carrier, R pThe inclination radius of representing first small gear of single small gear or compound gear, R p' the inclination radius of second small gear of expression compound gear.Number in the round parentheses refers to the value of A in the specific design.Can be found out obviously that by table 2 in traditional three kinds of patterns with in according to embodiments of the invention 1, determining of A value is different, this has shown the different performance of every kind of conveying means.Having the following advantages aspect the flexibility of design according to embodiments of the invention.For example, station wagon (air displacement is approximately 800cc) needs 0.06 to 0.25 OSR as the Matiz (trade mark) of Daewoo Motors.Usually, when the transmission system of the PGU shown in Figure 14 (c) has been used in configuration, to design this system be suitable so as the value of A between 0.06 and 0.25, preferred 0.18.Can see by Fig. 2,, can not design suitable PGU and be used to dispose transmission system to obtain the proper A value by traditional mode 1 and 3.On the other hand, advance attenuator (amplifier) and be used for to obtain the design load in the round parentheses in the table 2 if traditional mode 2 has single step towards inverted orientation between the load of the parts (connecting element or tie point) of load and conveying system.In according to embodiments of the invention 1, need not any additional device just can acquisition table 2 in design load in the round parentheses.Further, according to the present invention, if by according to other possible embodiments of the present invention and/or additional fixture, other decision design values can obtain as required, the flexibility that can obtain to design.In addition, the design load of traditional mode 2 is compared relative big with embodiment 1 design load.Less design load means that the size of transmission becomes littler, if consider factors such as expending of the weight of system and fuel, this is a good advantage.Like this, compare, used the transmission system according to embodiments of the invention of power distribution unit in actual design, to have significant flexibility with two sun gears, a carrier and at least one compound small gear with the traditional mode that uses a PGU.In addition, it more helps producing as little type.
With reference to Figure 15 to 17, be used for being illustrated according to the structure of two PGU of PSTS of the present invention.PGU1 or PGU2 can be the gear linkage units, and this gear linkage unit comprises a sun gear, a ring gear, a single or compound small gear and a carrier; Or the gear connection, this gear connects and comprises two sun gears, at least one compound small gear and a carrier; Or the gear that comprises two ring gears, at least one compound small gear and a carrier is connected.In PGU1 or PGU2, in three connecting element two but not small gear interosculate to form two tie points (C and D).Power source 1 and load 2 are connected respectively to two and keep connecting element A and B.Transmission 100 is connected as shown in figure 15 between the connecting element and tie point C of power source A, or is connected tie point C as shown in figure 16 and between the connecting element B of load side, or is connected as shown in figure 17 between two tie point C and the D.
Like this, because the difference in being connected of the I/O parts that tie point C and D and connecting element A and B are connected to power source and load or CVU comprises that the performance of traditional transmission system of two PGU just is different from the transmission system that comprises two PGU according to of the present invention on the whole.
Below equation 4 expression traditional modes in when PGU1 and 2 is represented as black box, the relation of VSR (ρ) and OSR (δ) and VPR (ρ) and OSR (δ):
ρ = C ( δ - B ) δ - A , ψ = ( A - δ ) ( δ - B ) ( A + B ) δ [equation 4]
Wherein A, B and C are the systematic parameters of determining according to type, size and the connecting means of the parts among PGU1 and the PGU2 respectively.If PGU is connected as described herein like that with CVU, equation 4 can be changed into following equation 5:
ρ = Aδ - CB δ - C , ψ = ( C - δ ) ( Aδ - CB ) C ( A + B ) δ [equation 5]
From the variation between equation 4 and 5,, can see easily that in above two kinds of situation underdrive performances be diverse by the analysis similar to the transmission that comprises a PGU.
Aforesaidly various fields can be used to, the machine of each generic request velocity variations function can be provided for according to CVT device of the present invention and power division CVT system.In according to traction drive CVT device of the present invention, come from people's (being used for bicycle), the power of motor (being used for motorcycle, automobile etc.) or motor (being used for industrial machine, robot, toy etc.) as power source directly or be applied in driving rotor, additional device such as clutch, torque converter or the attenuator (amplifier) of the input side of CVT device by additional device.
For the driven rotor of the outlet side of CVT device, load (such as wheel or cardan shaft or be used for the axle of movable robot's arm and similar thing etc.) is by direct or be connected by fixture such as difference gear or attenuator (amplifier) etc.In power division CVT device, power source is connected with the power distribution unit that comprises PGU with load, also is connected with power distribution unit at the rotor of the I/O side of CVT device.Not only can be used in automobile, industrial machine or require high-power large-scale robot according to CVT device of the present invention or power division CVT device, also can be used in the not too high or lower powered middle-size and small-size motorcycle of requirement, robot or bicycle, also can be used in the automobile of controlled in wireless or toy as requiring the typical doll of relative smaller power.In addition, owing to utilize staff or pin can easily equip simple and mechanical device as the mechanical device of power source, the present invention also can easily be used to sports equipment such as fitness equipment.Especially, have the following advantages according to conveying system of the present invention: thus when travelling on rugged mountain area and will often change speed, can reduce the overload of machine.Therefore, this conveying system can be used to military vehicle, for example tank or armored vehicle.
As mentioned above, improved traditional traction drive CVT device, therefore increased Maximum Torque, can realize accurate speed controlling, and the velocity ratio of the wide range that is suitable for power distribution unit is arranged according to CVT device of the present invention.
Especially, can obtain following effect according to CVT device of the present invention: regulate the position of counter-rotating rotor assembly by using four pole crank mechanisms, the counter-rotating rotor assembly can accurately be moved to desired position, stable contact condition can be kept, thereby needed velocity ratio can be easily obtained.The position of the pivot by making four pole crank mechanisms is consistent with all centre of rotor, contact segment always can not rely on four pole crank mechanisms crank the position and stably keep reliable.By between the spherical surface of rotor and counter-rotating rotor assembly, obtaining the configuration of outer spherical surface-inner ball surface contact or inner ball surface-outer spherical surface contact, contact area has been widened, the steady flow of oil film is held, and the application of fluid viscosity is maximized, thereby Maximum Torque is increased.Also the spherical surface of rotor that drives the two ends of rotor, driven rotor and counter-rotating rotor assembly freely can be designed to the inside or outside at rotor.The advantage that flexibility is arranged at design aspect according to CVT device of the present invention: can easily satisfy the specific requirement of machine.According to conveying means of the present invention, speed changer can break away from power distribution unit independently to be used.Since in the spherical surface contact between driving rotor and connection rotor and driven rotor and connection rotor can obtain-and outer or opposite contact, Maximum Torque is enhanced significantly.By adopting four pole crank mechanisms, the velocity variations scope is widened, thereby although according to speed changer of the present invention by independent utilization, also can obtain desired performance.
In according to power delivery system of the present invention, because when realizing the transmission system that the power division effect is significantly improved, also can guarantee to comprise the power distribution unit of one or two PGU and the flexibility of design, therefore obtain aspect the desired optimum OSR scope of transmission system greater flexibility is arranged according to power division transmission system of the present invention.Especially, in four port systems, two PGU are combined, when shown in Figure 15 to 17, when port A and port B are chosen as the I/O parts, can realize with traditional approach in the different conveying function of conveying function when selecting port C and port D, thereby realize the change of transmission device.
If to construct transmission system, so with the mode that merges according to traction drive CVT device of the present invention: the first, make the minimum power that is sent to the CVT device by the velocity range that maximizes the CVT device; Second, utilize the velocity variations scope of four pole crank mechanisms by making the CVT device to change on the occasion of then to infinity from negative value, can construct unlimited variable transmission device, wherein not need clutch or torque converter just can reach backward, stop and motion forward.In the embodiments of the invention shown in Figure 14 (c), with the pointed difference of data declaration, if OSR changes to 0.25 from-0.07 ,-0.07 expression motion backward, 0.0 expression neutral position travels forward on the occasion of expression.Figure 19 shows between the VSR of the embodiments of the invention in explanation Figure 14 (c) and the OSR and concerns performance curve.In this chart, change to 0.00 the process from-0.07 at OSR, VSR have on the occasion of, afterwards through 0, reduce to negative value more monotonously.Thus, when gear transmits when reaching systematic parameter A (being designed to 0.18 in this embodiment), VSR becomes negative infinity, is kept to positive finite value from positive infinity then.Promptly, the most significant advantage of the present invention is to obtain following CVT device easily: as mentioned above by means of aforementioned four pole crank mechanisms and spherical friction wheel, change to 0.25 the process from-0.07 at the OSR transmission process, wherein CVT device pinion ratio can be from the occasion of through 0 to negative infinitely great, then can from positive infinity to limited on the occasion of.

Claims (35)

1. one kind is used for changing and transmit traction drive continuous variable transmission (CVT) device of importing rotating force continuously in transmission system, comprising:
Be transfused to the driving rotor of rotating force rotation, at least one part on its surface has first spherical surface;
Accept the rotating force of self-driven rotor and the driven rotor that is rotated by the described rotating force from described driving rotor, at least one part on its surface has second spherical surface;
The counter-rotating rotor assembly, have the counter-rotating rotor of driving and driven counter-rotating rotor, be used for the rotating force between relaying driving rotor and the driven rotor, at least one part on the surface of described driving counter-rotating rotor has the 3rd spherical surface, with by driving the rotor traction drive, at least one part on described driven counter-rotating rotor surface has the 4th spherical surface with by the driven rotor traction drive; And
Four pole crank mechanisms have the rotatable counter-rotating rotor assembly that is fixed thereon, and are used to regulate the position of counter-rotating rotor assembly.
2. device as claimed in claim 1, wherein said four pole crank mechanisms comprise:
Fixing connecting rod is fixed in the framework of described CVT device;
Crank has the rotatable pivot and first joint, and described pivot is fixed in an end of described stationary links, and described first joint is fixed in the other end of described stationary links, and described crank is used for position regulation;
Rotary connector, an end are fixed in first joint of described crank, and the other end has second joint, and described rotatable counter-rotating rotor assembly is fixed in described connector; And
Rotatable follower is fixed in second joint of described connector, has the second rotatable pivot, and the described second rotatable pivot is fixed in the other end of described fixing connecting rod, and described follower is according to the motion of described crank and movable;
Wherein said counter-rotating rotor assembly has coupling shaft, be used for the driving counter-rotating rotor is connected to driven counter-rotating rotor so that they rotate together, wherein said coupling shaft is configured to quill shaft, and the connector of described rotatable four pole crank mechanisms is fixed in the described quill shaft.
3. device as claimed in claim 2, described first pivot of wherein said four pole crank mechanisms are positioned at the center of the spherical surface (described first spherical surface) of described driving rotor;
Described second pivot is positioned at the center of the spherical surface (described second spherical surface) of described driven rotor;
Under being positioned at, described first joint drives the center of the spherical surface (described the 3rd spherical surface) of counter-rotating rotor; And described second joint is positioned at the center of the spherical surface (described the 4th spherical surface) of described driven counter-rotating rotor.
4. device as claimed in claim 1, the described spherical surface of wherein said driving rotor is an inner ball surface;
The described spherical surface of described driving counter-rotating rotor is an outer spherical surface;
The described spherical surface of described driven counter-rotating rotor is an outer spherical surface;
The described spherical surface of described driven rotor is an inner ball surface.
5. device as claimed in claim 1, the described spherical surface of wherein said driving rotor is an outer spherical surface;
The described spherical surface of described driving counter-rotating rotor is an inner ball surface;
The described spherical surface of described driven counter-rotating rotor is an inner ball surface;
The described spherical surface of described driven rotor is an outer spherical surface.
6. device as claimed in claim 1, the described spherical surface of wherein said driving rotor is an outer spherical surface;
The described spherical surface of described driving counter-rotating rotor is an outer spherical surface;
The described spherical surface of described driven counter-rotating rotor is an outer spherical surface;
The described spherical surface of described driven rotor is an outer spherical surface.
7. device as claimed in claim 1, the described spherical surface of wherein said driving rotor is an inner ball surface;
The described spherical surface of described driving counter-rotating rotor is an outer spherical surface;
The described spherical surface of described driven counter-rotating rotor is an inner ball surface;
The described spherical surface of described driven rotor is an outer spherical surface.
8. device as claimed in claim 1, the described spherical surface of wherein said driving rotor is an outer spherical surface;
The described spherical surface of described driving counter-rotating rotor is an inner ball surface;
The described spherical surface of described driven counter-rotating rotor is an outer spherical surface;
The described spherical surface of described driven rotor is an inner ball surface.
9. device as claimed in claim 1, the described spherical surface of wherein said driving rotor is an inner ball surface;
The described spherical surface of described driving counter-rotating rotor is an outer spherical surface;
The described spherical surface of described driven counter-rotating rotor is an outer spherical surface;
The described spherical surface of described driven rotor is an outer spherical surface.
10. device as claimed in claim 1, the described spherical surface of wherein said driving rotor is an outer spherical surface;
The described spherical surface of described driving counter-rotating rotor is an outer spherical surface;
The described spherical surface of described driven counter-rotating rotor is an outer spherical surface;
The described spherical surface of described driven rotor is an inner ball surface.
11. device as claimed in claim 1, the described spherical surface of wherein said driving rotor is an outer spherical surface;
The described spherical surface of described driving counter-rotating rotor is an inner ball surface;
The described spherical surface of described driven counter-rotating rotor is an outer spherical surface;
The described spherical surface of described driven rotor is an outer spherical surface.
12. device as claimed in claim 1, the described spherical surface of wherein said driving rotor is an outer spherical surface;
The described spherical surface of described driving counter-rotating rotor is an outer spherical surface;
The described spherical surface of described driven counter-rotating rotor is an inner ball surface;
The described spherical surface of described driven rotor is an outer spherical surface.
13. the power division transmission system of a power conversion unit comprises:
Power distribution unit, comprise planetary gear unit (PGU), described planetary gear unit or comprise at least one compound small gear, two sun gears and a carrier as outer connecting element as internal connecting element, perhaps comprise at least one compound small gear as internal connecting element, two ring gears and the carrier as outer connecting element, described planetary gear unit is used for input Power Distribution to two paths, transmission and exports this power; And
Transmission device, itself or stepping variable drive assembly or continuous variable transmission (CVT) device are used to receive from the part that is assigned with power of power distribution unit and with the rotating force conversion and be transmitted back to power distribution unit.
14. system as claimed in claim 13, first connecting element of wherein said PGU directly or by attenuator (amplifier) is connected to power source;
Second connecting element of described PGU directly or by attenuator (amplifier) is connected to load;
Described transmission device directly or be connected by attenuator (amplifier) between described first connecting element and described the 3rd connecting element of described PGU perhaps is connected between described the 3rd connecting element and described second connecting element.
15. system as claimed in claim 14, described first connecting element of wherein said PGU is a carrier, and described second connecting element is first sun gear, and described the 3rd connecting element is a secondary sun wheel; Described transmission device directly or by attenuator (amplifier) is connected between described the 3rd connecting element and described second connecting element.
16. the power division transmission system of a power conversion unit comprises:
Power distribution unit, have by the first gear link unit, second gear connects the combination of two PGU that are connected with the 3rd gear, the described first gear link unit has a sun gear, a ring gear, a single or compound small gear and a carrier, described second gear connection has two sun gears, at least one compound small gear and a carrier, described the 3rd gear connection has two ring gears, at least one small gear and a carrier, described power distribution unit is by using two PGU, input Power Distribution extremely more than one path, is transmitted and exports this power; And
Transmission device, itself or stepping variable drive assembly or CVT device are used to receive the part that is assigned with power from power distribution unit, and with the rotating force conversion and be transmitted back to power distribution unit,
Wherein the combination of two PGU comprises: first connecting element, and it is first parts of a PGU; Second connecting element, it is first parts of the 2nd PGU; First tie point, second parts by connecting a PGU and second parts of the 2nd PGU obtain; Second tie point, the 3rd parts by connecting a PGU and the 3rd parts of the 2nd PGU obtain.
17. system as claimed in claim 16, wherein first connecting element directly or by attenuator (amplifier) is connected to power source;
Second connecting element directly or by attenuator (amplifier) is connected to load; With
Transmission device directly or by attenuator (amplifier) is connected between described first connecting element and described first tie point, or between first tie point and second connecting element, or between first tie point and second tie point.
18. traction drive continuous variable transmission (CVT) system of a power conversion unit comprises: constantly variable transmission is used for changing continuously and transmitting the input rotating force; Power distribution unit comprises a PGU,
Wherein the transmission device of continuous variable comprises:
Drive rotor, can by the rotation of input rotating force or by with power distribution unit that described driving rotor is connected in the parts of PGU rotate, described driving rotor has first spherical surface at least one part on its surface;
Driven rotor, reception comes from the rotating force that drives rotor and is rotated, and described driven rotor has second spherical surface at least one part on its surface;
The counter-rotating rotor assembly, comprise and drive counter-rotating rotor and driven counter-rotating rotor, drive counter-rotating rotor and have the 3rd spherical surface at it by at least one part that drives rotor traction-driven surface, driven counter-rotating rotor has the 4th spherical surface in its at least one part by driven rotor traction-driven surface; And
Four pole crank mechanisms have rotatable counter-rotating rotor assembly and are fixed thereon, and are used to regulate the position of counter-rotating rotor assembly,
Wherein be used to provide the input rotating force power source, velocity variations the load that rotating force outputed to, drive rotor and driven rotor is connected with the PGU of power distribution unit, thereby only some is input to the driving rotor and is used for transmission the rotating force that is provided by power source.
19. system as claimed in claim 18, wherein four pole crank mechanisms comprise:
Fixing connecting rod is fixed in the framework that described continuous variable transmission (CVT) is installed;
Crank has the first rotatable pivot and first joint, and the described first rotatable pivot is fixed in an end of described stationary links, and described first joint is fixed in the other end of described stationary links, and described crank is used for position regulation;
Rotary connector, an end are fixed in first joint of described crank, and the other end has second joint, and described rotatable counter-rotating rotor assembly is fixed in described connector; And
Rotatable follower is fixed in second joint of described connector, has the second rotatable pivot, and the described second rotatable pivot is fixed in the other end of described fixing connecting rod, and described follower depends on the motion of crank and movable;
Wherein said counter-rotating rotor assembly has rotatable coupling shaft, be used for the driving counter-rotating rotor is connected to driven counter-rotating rotor so that they rotate together and
Wherein said coupling shaft is configured to quill shaft, and the connector of described rotatable four pole crank mechanisms is fixed in the described quill shaft.
20. system as claimed in claim 19, the described PGU of wherein said power distribution unit can be any one in the following type: have a carrier, two sun gears and a small gear, have a carrier, two ring gears and a small gear, have a carrier, two sun gears and two small gears, have a carrier, two ring gears and two small gears, have a carrier, a ring gear, a sun gear and two small gears
Wherein said power source, described load, described driving rotor and described driven rotor directly or by attenuator (amplifier) respectively with the small gear of PGU outside parts link.
21. system as claimed in claim 19, the wherein contact between the spherical surface of spherical surface that drives rotor and driving counter-rotating rotor, in the contact between the spherical surface of driven rotor and the spherical surface of driven counter-rotating rotor, at least one is that inner ball surface contacts with outer spherical surface or outer spherical surface contacts with inner ball surface.
22. system as claimed in claim 19, the contact that wherein drives the spherical surface of rotor and drive between the spherical surface of counter-rotating rotor is that outer spherical surface contacts with outer spherical surface, and the contact between the spherical surface of driven counter-rotating rotor and the spherical surface of driven rotor is that outer spherical surface contacts with outer spherical surface.
23. the traction drive Continuously Variable Transmission system of a power conversion unit comprises:
The CVT device is used for changing continuously and transmitting the input rotating force; And
Power distribution unit is made up of at least two PGU,
Wherein the CVT device comprises:
Drive rotor, can by the rotation of input rotating force or by with power distribution unit that described driving rotor is connected in the parts of PGU rotate, described driving rotor has first spherical surface at least one part on its surface;
Driven rotor, reception comes from the rotating force that drives rotor and is rotated, and described driven rotor has second spherical surface at least one part on its surface;
The counter-rotating rotor assembly, comprise and drive counter-rotating rotor and driven counter-rotating rotor, described driving counter-rotating rotor has the 3rd spherical surface in its at least one part by the spherical surface traction-driven surface that drives rotor, and described driven counter-rotating rotor has the 4th spherical surface in its at least one part by the spherical surface traction-driven surface of driven rotor; And
Four pole crank mechanisms are fixed with rotatable counter-rotating rotor assembly on it, be used to regulate the position of counter-rotating rotor assembly,
Wherein be used to provide the input rotating force power source, velocity variations the load that rotating force outputed to, drive rotor and driven rotor is connected with the PGU of power distribution unit, thereby only some is input to the driving rotor and is used for transmission the rotating force that is provided by power source.
24. system as claimed in claim 23, wherein four pole crank mechanisms comprise:
Fixing connecting rod is fixed in the framework of described CVT device;
Crank has the first rotatable pivot and first joint, and the described first rotatable pivot is fixed in an end of described stationary links, and described first joint is fixed in the other end of described stationary links, and described crank is used for position regulation;
Rotary connector, an end are fixed in first joint of described crank, and the other end has second joint, and described rotatable counter-rotating rotor assembly is fixed in described connector; And
Rotatable follower is fixed in second joint of described connector, has the second rotatable pivot, and the described second rotatable pivot is fixed in the other end of described fixing connecting rod, and described follower depends on the motion of crank and movable;
Wherein said counter-rotating rotor assembly has rotatable coupling shaft, is used for the driving counter-rotating rotor is connected to driven counter-rotating rotor so that they rotate together,
Wherein said coupling shaft is configured to quill shaft, and the connector of described rotatable four pole crank mechanisms is fixed in the described quill shaft.
25. system as claimed in claim 23, first pivot of wherein said four pole crank mechanisms is positioned at the center of the spherical surface that drives rotor;
Described second pivot is positioned at the center of the spherical surface of driven rotor;
Described first joint is positioned at the center of the spherical surface that drives counter-rotating rotor;
Described second joint is positioned at the center of the spherical surface of driven counter-rotating rotor.
26. system as claimed in claim 23, second pivot of wherein said four pole crank mechanisms is positioned at the center of the spherical surface that drives rotor;
Described second pivot is positioned at the center of the spherical surface of driven rotor;
Described second joint is positioned at the center of the spherical surface that drives counter-rotating rotor;
Described first joint is positioned at the center of the spherical surface of driven counter-rotating rotor.
27. system as claimed in claim 23, wherein power distribution unit comprises first and second planetary gear units, and first and second planetary gear units have a sun gear, a ring gear and a carrier separately as parts; Two parts among the described PGU are connected with two parts among described the 2nd PGU respectively; Power source is connected with a described PGU or described driving rotor, and described load is connected with described the 2nd PGU or described driven rotor, and at least one in described driving rotor and the driven rotor is connected with tie point between described first and second PGU.
28. system as claimed in claim 23, wherein drive the spherical surface of rotor and drive contact between the spherical surface of counter-rotating rotor, at least one is that inner ball surface contacts with outer spherical surface or outer spherical surface contacts with inner ball surface in the contact between the spherical surface of driven rotor and the spherical surface of driven counter-rotating rotor.
29. system as claimed in claim 23, the contact that wherein drives the spherical surface of rotor and drive between the spherical surface of counter-rotating rotor is that outer spherical surface contacts with outer spherical surface, and the contact between the spherical surface of driven counter-rotating rotor and the spherical surface of driven rotor is that outer spherical surface contacts with outer spherical surface.
30. a motorcycle comprises any one desired constantly variable transmission or transmission system in the claim 1 to 29.
31. an automobile comprises any one desired constantly variable transmission or transmission system in the claim 1 to 29.
32. an industrial machine comprises any one desired constantly variable transmission or transmission system in the claim 1 to 29.
33. a bicycle comprises any one desired constantly variable transmission or transmission system in the claim 1 to 29.
34. a toy comprises any one desired constantly variable transmission or transmission system in the claim 1 to 29.
35. a robot comprises any one desired constantly variable transmission or transmission system in the claim 1 to 29.
CNA028106865A 2001-05-26 2002-05-24 Traction continuously variable transmission device, split-power transmission system and apparatus using same Pending CN1511237A (en)

Applications Claiming Priority (6)

Application Number Priority Date Filing Date Title
KR1020010029266A KR20020090270A (en) 2001-05-26 2001-05-26 Power split type speed transmission system using multiple planetary gear unit and apparatus employing thereof
KR2001/29266 2001-05-26
KR10-2001-0041222A KR100422320B1 (en) 2001-07-10 2001-07-10 A power split type speed transmission system using a planetary gear unit and apparatus employing thereof
KR2001/41222 2001-07-10
KR10-2002-0014976A KR100426333B1 (en) 2002-03-20 2002-03-20 Traction drive continuously various transmission having a four bar linkage and spherical rotors
KR2002/14976 2002-03-20

Publications (1)

Publication Number Publication Date
CN1511237A true CN1511237A (en) 2004-07-07

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Application Number Title Priority Date Filing Date
CNA028106865A Pending CN1511237A (en) 2001-05-26 2002-05-24 Traction continuously variable transmission device, split-power transmission system and apparatus using same

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Country Link
CN (1) CN1511237A (en)
WO (1) WO2002097303A1 (en)

Cited By (1)

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CN106838190A (en) * 2016-12-21 2017-06-13 四川大学 A kind of parallel axes is without the towed buncher that spins

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JP4310362B2 (en) * 2006-12-28 2009-08-05 本田技研工業株式会社 Power equipment
WO2011081866A2 (en) * 2009-12-14 2011-07-07 Orbital Traction, Ltd. Systems and methods for operating a driveline system
US20190017583A1 (en) * 2016-01-13 2019-01-17 Dana Limited Four mode dual planetary powertrain configurations with a ball variator continuously variable transmission used as a powersplit

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US5711741A (en) * 1995-02-27 1998-01-27 Isuzu Motors Limited Fail safe for toroidal continuous variable transmission
JP3629773B2 (en) * 1995-09-29 2005-03-16 マツダ株式会社 Toroidal continuously variable transmission
JP2000314460A (en) * 1999-04-30 2000-11-14 Honda Motor Co Ltd Toroidal type continuosly variable transmission

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN106838190A (en) * 2016-12-21 2017-06-13 四川大学 A kind of parallel axes is without the towed buncher that spins
CN106838190B (en) * 2016-12-21 2019-05-17 四川大学 A kind of parallel axes is without the towed stepless transmission that spins

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