CN100434755C

CN100434755C - Pulsating stepless transmission

Info

Publication number: CN100434755C
Application number: CNB2005100942437A
Authority: CN
Inventors: 吴华峰
Original assignee: Individual
Current assignee: Individual
Priority date: 2005-09-06
Filing date: 2005-09-06
Publication date: 2008-11-19
Anticipated expiration: 2025-09-06
Also published as: CN1800674A; WO2007028318A1

Abstract

The present invention relates to a pulsating movement stepless speed changer which adopts the structure that one end of a transmission mechanism which is designed according to an ' equal line speed homodromous overturn homothetic performance principle ', the other end of the transmission mechanism and an input shaft of the pulsating movement stepless speed changer respectively seal two center wheels of a differential gear train of a bevel gear of a 2Z-X type positive sign mechanism of which the transmitting ratio is one to one, a rotary arm outputs dynamic force, and a combined mechanism which has phase separation of 180 DEG outputs the dynamic force according to each phase. The pulsating movement stepless speed changer overcomes the relevant critical defects of a traditional pulsating movement stepless speed changer, weak links do not exist in the dynamic force chain of an entire gearing, and the potentiality of each link can be farthest performed. The present invention has the advantages of reasonable structure, easy and convenient control, economy, high efficiency, high bearing capacity, wide range of speed change and precise and smooth output of torquemoment, and is especially suitable for a vehicle with high speed and large power, particularly the speed change system of the vehicle.

Description

Impulse stepless gear box

Technical field

The present invention relates to mechanical stepless transmission, specifically, relate to a kind of impulse stepless gear box.

Background technique

As everyone knows, the tradition impulse stepless gear box adopts driving mechanism to convert the uniform speed rotation of transmission main shaft to be applied on the mono-directional overrun clutch speed change and rotatablely moves, and then rotatablely moves through the unidirectional pulsating nature that mono-directional overrun clutch converts output shaft to; By several combined mechanisms, make output shaft obtain the very little unidirectional rotary motion of ripple amplitude with certain phase difference.The throw of eccentric that changes a certain member length in the driving mechanism or change a certain member with speed regulating mechanism forms dimension scale relation new between member, thereby change the rate of change of angular that speed change rotatablely moves, by free wheel device the rotating speed of output shaft is changed, thereby reach infinite variable speed purpose.At Ruan Zhongtang chief editor's " mechanical stepless transmission design and guide ", made detailed description in the specification of Chinese patent publication number CN2128983Y and CN2078823Y.

The shortcoming of tradition impulse stepless gear box is limited by the bearing capacity of mono-directional overrun clutch and impact resistance, and output mechanism becomes the critical defect of traditional impulse stepless gear box, therefore can only be applicable to the low speed middle low power.And mono-directional overrun clutch can only be with the power output of that sets of transmission mechanism of instantaneous angular velocity maximum, and pulsating nature is bigger, reduces pulsation with the methods that increase the combined mechanism numbers of phases more, can make the impulse stepless gear box structure be tending towards complicated again.

Summary of the invention

The present invention is directed to the problems referred to above that prior art exists, a kind of impulse stepless gear box is provided, its technical problem that will solve is: change the method for being come transferring power in traditional impulse stepless gear box by free wheel device as the output mechanism critical piece.Replace free wheel device with other member and come outputting power, make entire mechanism power transmission chain Weak link-free, and can cooperate with driving mechanism during outputting power the speed change that driving mechanism is transformed into rotatablely move in the less that part of transmission of power of angular velocity varies give output shaft, reduce the pulsating nature of outputting power.

Technological scheme of the present invention is achieved in that and adopts 2Z-X type positive sign mechanism differential gear train as output mechanism, after the driving mechanism input end of speed changer connects transmission input shaft, use two central gears of the input and output side difference deblocking 2Z-X type positive sign mechanism differential gear train of driving mechanism again, by the pivoted arm outputting power; With two or more combinations with the driving mechanism of certain phase difference and differential gear train by outputting power mutually; Utilize differential gear train to pursue when exporting mutually,, export, reach the effect that reduces output ripple with driving mechanism and the differential gear train that part of power that rotation speed change is less of working in coordination not necessarily with the characteristics of power output of that cover mechanism of angular velocity maximum.

In a preferred embodiment of this invention: 2Z-X type positive sign mechanism differential gear train is 1: 1 a cone gear differential gear train of velocity ratio, and pivoted arm adopts single dual cone gears form; Include in the driving mechanism by with the joining concentric drums of differential gear train central gear be enclosed within the camcylinder of concentric drums outside, under the controlling mechanism effect, camcylinder can change the degree of eccentricity with concentric drums; The helical teeth that an identical rotation direction is respectively arranged on camcylinder inwall and the concentric drums outer wall, helical teeth on the camcylinder has a fixing helix angle, helical teeth on the concentric drums is apart from corresponding fixing helix angle of the flank of tooth of the center same radius of concentric drums, along with the helical teeth flank of tooth and concentric drums center radius distance is big more, the helix angle of the corresponding flank of tooth evenly reduces on the helical teeth.

Impulse stepless gear box of the present invention has been compared following advantage with traditional impulse stepless gear box: owing to adopted driving mechanism planetary differential central gear to come outputting power, no longer adopt free wheel device, make whole impulse stepless gear box power transmission chain Weak link-free, can bring into play each link potential to greatest extent, improved the reliability of impulse stepless gear box, bearing capacity and impact resistance make impulse stepless gear box can apply to high-speed high-power.That less a part of power output of angular velocity varies makes impulse stepless gear box output steadily, stable performance in the speed change rotation fortune after combined mechanism transforms driving mechanism simultaneously.

Description of drawings

Below in conjunction with accompanying drawing the specific embodiment of the present invention is described in further detail:

Fig. 1 is the structural principle sketch of the embodiment of the invention;

Fig. 2 is an A-A sectional view among Fig. 1;

Fig. 3 is a B-B sectional view among Fig. 1.

Among the figure: 1, input shaft, 2, the input shaft cylinder, 3, output shaft, 4, bearing, 5, bearing, 6, bearing, 7, bearing, 8, housing, 9, central gear, 10, pivoted arm, 11, central gear, 12, pivoted arm, 13, central gear, 14, preceding concentric drums, 15, the back concentric drums, 16, camcylinder, 17, coupling, 18, the camcylinder support, 19, camcylinder support shaft, 20, output gear, 21, the camcylinder controlling mechanism, 22, semi-circle gear, 23, helical teeth, 24, helical teeth, 25, spring, 26, straight-tooth, 27, straight-tooth, 28, straight-tooth, 29, straight-tooth.

Specific implementation method

Accompanying drawing discloses the concrete structure of one embodiment of the invention without limitation, and the present invention is further detailed explanation below in conjunction with accompanying drawing:

As seen from Figure 1, input shaft 1 of the present invention reaches the input shaft cylinder 2 and the output shaft 3 that are solidified as a whole with input shaft 1 and keeps concentric, and they are bearing on the housing 8 by bearing 6,7, and input shaft 1 and output shaft 3 support mutually by bearing 4; Form two groups of 2Z-X type positive sign mechanism cone gear differential gear trains (the shared central gear 11 of two cone gear difference trains) by central gear 9, pivoted arm 10, central gear 11 and central gear 11, pivoted arm 12, central gear 13 with two-sided awl tooth, the velocity ratio of every group of 2Z-X type positive sign mechanism cone gear differential gear train is 1: 1, and central gear 11 combines as a whole with input shaft cylinder 2, and central gear 11 is sleeved on the output shaft 3 by bearing 5.Preceding concentric drums 14 and the back concentric drums 15 concentric with input shaft 1 output shaft 3 combine as a whole with central gear 9 and central gear 13 respectively, and they all are contained on the output shaft 3 by bearing housing.Pivoted arm 10 and pivoted arm 12 also are contained on the output shaft 3 by bearing housing; Camcylinder 16 passes through can keep connecting with input shaft cylinder 2 with the coupling 17 of input shaft 1 isogonism speed, and is enclosed within the outside of input shaft cylinder 2.Camcylinder 16 by bearing fixing on camcylinder support 18, camcylinder support 18 by bearing fixing on camcylinder support shaft 19, camcylinder support shaft 19 combines as a whole with housing 8, camcylinder controlling mechanism 21 is fixed on the housing 8, the output gear 20 of camcylinder controlling mechanism 21 is engaged with the semi-circle gear 22 on the camcylinder support 18, camcylinder controlling mechanism 21 can drive semi-circle gear 22 by output gear 20 and rotate, thereby drive camcylinder support 18 and on camcylinder 16 rotates within the specific limits around camcylinder support shaft 19, make camcylinder 16 and input shaft cylinder 2 and preceding concentric drums 14, back concentric drums 15 forms the different degree of eccentricitys.

Shown in Figure 2, camcylinder 16 inner circumferences are provided with the helical teeth 23 with certain helix angle, have a skewed slot with helical teeth 23 corresponding positions on the input shaft cylinder 2 with certain width, can insert for helical teeth 23, input shaft cylinder 2, on the excircle of preceding concentric drums 14, also have a helical teeth 24 identical with helical teeth 23 rotation directions, on the helical teeth 24 apart from corresponding fixing helix angle of the flank of tooth of the center same radius of concentric drums, along with the helical teeth flank of tooth and concentric drums center radius distance is big more, the helix angle of the corresponding flank of tooth evenly reduces on the helical teeth.Current concentric drums 14 and camcylinder 16 is with one heart the time, and helical teeth 24 and helical teeth 23 can fit tightly to the tooth tail from increment, and the helix angle of helical teeth 24 flank of tooth of this moment equals the helix angle of helical teeth 23, and this moment helical teeth 23 and helical teeth 24 tooth appearance etc.; The actual tooth root of helical teeth 24 tooth tails thick with the л of the flank of tooth place of helical teeth 24 difference that the due tooth root of tooth tail is thick when having helical teeth 23 same-handed angles when having the same-handed angle with helical teeth 23 on helical teeth 24 flank of tooth to preceding concentric drums 14 radius centered and helical teeth 24 tooth roots to preceding concentric drums 14 center radius differences doubly.Be provided with a spring 25 between input shaft cylinder 2 and preceding concentric drums 14, the elastic force of spring 25 can support moment much smaller than the input shaft input torque, and spring 25 can make helical teeth 23 and helical teeth 24 fit as far as possible.Equally, back concentric drums 15 is identical with preceding concentric drums 14 with the interconnected relationship of facing parts mutually: on back concentric drums 15 and camcylinder 16 corresponding helical teeth is arranged also, also be provided with spring between input shaft cylinder 2 and the back concentric drums 15.180 ° of two helical teeth phases phase differences on the camcylinder 16.

As shown in Figure 3, pivoted arm 10 is provided with the straight-

tooth

28 and 29 of two symmetries, the also corresponding straight-

tooth

26 and 27 that is provided with two symmetries on the output shaft 3.Pivoted arm 10 can be by the straight-tooth 27 on the straight-tooth 28 promotion output shafts 3 during proper functioning, and straight-tooth 29 promotes straight-tooth 26 and drives output shafts 3 rotation outputting powers.Simultaneously, pivoted arm 12 and also be provided with the straight-tooth of effect with it on the output shaft 3 of corresponding position with it; All can relatively rotate within the specific limits between output shaft 3 and pivoted arm 10 and output shaft 3 and the pivoted arm 12, rotatable angle is generally about 90 °.

Working principle of the present invention based on: by 1: 1 2Z-X type bevel gear positive sign mechanism differential gear train characteristic of velocity ratio as can be known, two central gears turn to same rotational speed unequal the time, pivoted arm will be in the state that rotatablely moves with the central gear switched in opposite.In the present invention, input shaft cylinder 2 connects with central gear 11, make central gear 11 rotating speeds equal input speed all the time, forward and backward concentric drums 14 and 15 connects with another central gear 9 and 13, forward and backward concentric drums 14 and 15 is subjected to camcylinder 16 controls (referring to Fig. 1), as long as forward and backward concentric drums 14 and 15 when rotating speed and input shaft cylinder 2 rotating speeds are inconsistent, will make pivoted arm 10 and 12 reverse outputting powers under camcylinder 16 promotes.Because two central gears of differential gear train are sealed by driving mechanism, be added in two moments on the central gear during pivoted arm outputting power and be in a kind of bootstrapping state, as long as the rotating speed of two central gears is inconsistent, be added in two moments on the central gear and all become with the absolute value of the speed discrepancy of two central gears and reduce greatly, promptly the moment of pivoted arm outputting power can become corresponding diminishing greatly with the speed of pivoted arm.

In an embodiment of the present invention:

When camcylinder 16 is under the adjusting of camcylinder controlling mechanism 21 with input shaft cylinder 2 when concentric, power is by input shaft 1 input, make input shaft cylinder 2 by coupling 17 drive camcylinders 16 with one fixedly sense of rotation rotate.Concentric drums 14 and back concentric drums 15 rotated in the same way before camcylinder 16 drove simultaneously by the helical teeth on it again, because concentric drums 14 and back concentric drums 15 are concentric with input shaft cylinder 2 before this moment, the rotating speed of concentric drums 14 and back concentric drums 15 equals the rotating speed of camcylinder 16 and input shaft cylinder 2 before this moment, pivoted arm 10 and pivoted arm 12 remain static, output shaft 3 unpowered outputs, impulse stepless gear box is in the zero output state.

When camcylinder 16 under the adjusting of camcylinder controlling mechanism 21, camcylinder 16 and input shaft cylinder 2, preceding concentric drums 14 and back concentric drums 15 have certain degree of eccentricity, by the geometric position of camcylinder 16 and concentric drums 14 as can be known, variation has taken place in the point of action (face) that helical teeth 23 and helical teeth 24 promotes mutually, and the л of the flank of tooth place of the due tooth root of tooth tail is thick when having helical teeth 23 same-handed angles with helical teeth 24 difference that the actual tooth root of helical teeth 24 tooth tails is thick when having the same-handed angle with helical teeth 23 on helical teeth 24 flank of tooth to preceding concentric drums 14 radius centered and helical teeth 24 tooth roots to preceding concentric drums 14 center radius differences doubly.Therefore the promotion point (face) of helical teeth 23 increments and helical teeth 24 increments is in along the preceding concentric drums of input shaft cylinder 2 sense of rotation helical teeth 23 tooth tops distance 14 centers a certain position the most nearby, helical teeth 23 is located linear speed Equidirectional overturnings such as linear velocity with helical teeth 24 to promote point (face), increment when promotion point (face) touched from rigidly connecting when helical teeth 23 promoted mutually with helical teeth 24 promotes point (face) and is in similar geometric position all the time until the tooth tail constantly changes.When helical teeth 23 promoted upset mutually with helical teeth 24, concentric drums 14 can keep a certain uniform motion greater than input shaft cylinder 2 rotating speeds, pivoted arm 16 reverse uniform rotation outputting powers.Along with helical teeth 23 and helical teeth 24 do not stop the upset, the angular pitch of helical teeth 23 and helical teeth 24 is from continuing to increase, the tooth tail is constantly approaching, when promotion point (face) changes to the tooth tail, the promotion point (face) of helical teeth 23 and helical teeth 24 will no longer can remain on similar geometric position, before concentric drums 14 motion that also no longer remains a constant speed, according to the geometry site of camcylinder 16 and preceding concentric drums 14 as can be known, preceding concentric drums 14 will be in rapid deceleration regime.Current concentric drums 14 rotating speeds are during less than the rotating speed of camcylinder 16, the elastic force institute energy support force distance of spring 25 is much smaller than input shaft moment, power after the conversion can't make pivoted arm 10 promote output shaft 3 and rotate, therefore the rotating speed that has only preceding concentric drums 14 during proper functioning is during greater than camcylinder 16 rotating speeds, and pivoted arm 10 could promote output shaft 3 rotations.Because promoting concentric drums 14 for 360 °, camcylinder 16 rotations also rotate 360 °, therefore when concentric drums 14 rotating speeds are greater than camcylinder 16 rotating speeds before, preceding concentric drums 14 and input shaft cylinder 2 outer corner differences and preceding concentric drums 14 rotating speeds during less than camcylinder 16 rotating speeds input shaft cylinder 2 equate with the outer corner difference of preceding concentric drums 14.In case the rotating speed of preceding concentric drums 14 is just less than the rotating speed of camcylinder 16, will by the combined mechanism of forming with input shaft cylinder 2, preceding concentric drums 14 and central gear 9 and 11, pivoted arm 10 mutually the combined mechanism of forming by input shaft cylinder 2, back concentric drums 15 and central gear 11 and 13, pivoted arm 12 of 180 ° of phase differences under the promotion of camcylinder 16, pursue the phase outputting power by output shaft 3.3 overwhelming majority times of output shaft can maintain at the uniform velocity state.

Concrete running state is as follows: when concentric drums 14 is at the uniform velocity state before in the combined mechanism that input shaft cylinder 2, preceding concentric drums 14 and central gear 9 and 11, pivoted arm 10 are formed, pivoted arm 10 at the uniform velocity promotes output shaft 3 uniform rotation, current concentric drums 14 is when at the uniform velocity state slows down rapidly, pivoted arm 10 slowly slows down under effect of inertia, and straight-tooth 28 on the pivoted arm 10 and the distance between the straight-tooth 27 on the output shaft 3 strengthen gradually.The rotating speed of current concentric drums 14 is during just less than input shaft cylinder 2 rotating speeds, and the combined mechanism that input shaft cylinder 2, back concentric drums 15 and central gear 11 and 13, pivoted arm 12 are formed continues to promote output shaft 3 and keeps at the uniform velocity state.Since preceding concentric drums 14 rotating speeds during just less than input shaft cylinder 2 rotating speeds the rotating speed lowering speed big especially, straight-tooth 28 on the pivoted arm 10 and the distance between the straight-tooth 27 on the output shaft 3 are constantly reduced, until applying.After straight-tooth 28 and straight-tooth 27 were fitted, the tooth tail of helical teeth 23 and helical teeth 24 began to separate, and no longer fits.Rotation along with camcylinder 16 and preceding concentric drums 14, the tooth tail of helical teeth 23 and helical teeth 24 remains on separated state always, the increment of helical teeth 23 and helical teeth 24 is constantly approaching, until applying, promote mutually, replace the combined mechanism outputting power of input shaft cylinder 2, back concentric drums 15 and central gear 11 and 13, pivoted arm 10 compositions.Circulation makes the impulse stepless gear box continuous running and so forth.

Along with camcylinder 16 under the adjusting of camcylinder controlling mechanism 21, when the degree of eccentricity of camcylinder 16 and input shaft cylinder 2 strengthens, helical teeth on the camcylinder 16 and the helical teeth on the concentric drums promote the constantly change of the helical teeth root on concentric drums of point (face), because the helical teeth flank of tooth on the concentric drums is big more to the root helix angle more, rotating speed when making the concentric drums uniform rotation is big more, rotating speed during the pivoted arm uniform rotation also constantly increases, also constantly increase by the rotating speed of exporting rear output shaft 3 mutually, realized the stepless change transmission.

In the actual design, helical teeth on camcylinder 16, the forward and backward concentric drums 14,15 can be designed to the axial stress that herringbone tooth or other shape reduce forward and backward concentric drums 14,15 and camcylinder 16, so that adopt short forward and backward concentric drums 14 and 15, camcylinder 16, input shaft cylinder 2, reduce the volume of impulse stepless gear box.

Preferred implementation of the present invention is useful for vehicle gear box.Should be understood that; for the person of ordinary skill of the art; under the prerequisite that does not break away from the principle of the invention; also can make some distortion and improvement; particularly adopt other kind differential gear trains of similar functions to realize the output mechanism function of impulse stepless gear box device, these also should be considered as belonging to protection scope of the present invention.

Claims

1, a kind of impulse stepless gear box, by the uniform speed rotation being converted to the driving mechanism that speed change rotatablely moves, the speed regulating mechanism of dimension scale relation is formed between the output mechanism of outputting power and change driving mechanism member, it is characterized in that: impulse stepless gear box 2Z-X type positive sign mechanism differential gear train is as output mechanism, by two central gears of driving mechanism input and output side difference deblocking 2Z-X type positive sign mechanism differential gear train, by the pivoted arm outputting power; With two or more combinations with the driving mechanism of certain phase difference and differential gear train by outputting power mutually.

2, the described impulse stepless gear box of claim 1 is characterized in that: the 2Z-X type positive sign mechanism differential gear train that impulse stepless gear box adopts is 1: 1 a 2Z-X type positive sign mechanism cone gear differential gear train of velocity ratio, and pivoted arm adopts single dual cone gears form.

3, the described impulse stepless gear box of claim 1 is characterized in that: include in the driving mechanism of impulse stepless gear box by with the joining concentric drums of differential gear train central gear be enclosed within the camcylinder of concentric drums outside, under the controlling mechanism effect, camcylinder can change the degree of eccentricity with concentric drums; The helical teeth that an identical rotation direction is respectively arranged on camcylinder inwall and the concentric drums outer wall.

4, the described impulse stepless gear box of claim 1 is characterized in that: in the impulse stepless gear box on the helical teeth of concentric drums apart from corresponding fixing helix angle of the flank of tooth of the center same radius of concentric drums, along with the helical teeth flank of tooth and concentric drums center radius distance is big more, the helix angle of the corresponding flank of tooth evenly reduces on the helical teeth.