CN113685514A - Single-side input and output three-planet-row stepless speed change mechanism and speed change method thereof - Google Patents
Single-side input and output three-planet-row stepless speed change mechanism and speed change method thereof Download PDFInfo
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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
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
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Abstract
The invention discloses a unilateral input and output three-planet-row stepless speed change mechanism and a speed change method thereof, belonging to the technical field of stepless speed changers. According to the single-side input and output three-planet-row stepless speed change mechanism, the connecting ends of the first driving piece, the second driving piece and the output part are all arranged at one end of the stepless speed change mechanism, so that the power is input and output at one end of the stepless speed change mechanism, and the whole power equipment is more reasonable in arrangement and space utilization rate.
Description
Technical Field
The invention relates to the technical field of continuously variable transmissions, in particular to a single-side input and output three-planet-row continuously variable transmission mechanism and a speed change method thereof.
Background
With the higher and higher requirements of the society on environmental protection, the electric vehicle technology becomes the mainstream research direction of each large vehicle enterprise. At present, the electric vehicle mostly adopts a speed reducer with a fixed speed ratio, although the speed reducer with a large speed ratio can be selected to meet the power requirement when the vehicle starts and climbs, the large speed ratio limits the vehicle to be incapable of reaching a high maximum speed, and the reason that the maximum speed of the electric vehicle is generally lower than the maximum speed of a fuel vehicle on the market is also provided. In order to take account of the highest speed and the climbing capability of a vehicle, a plurality of vehicle enterprises begin to install AMT transmissions on electric vehicles, but the AMT transmissions belong to step-by-step speed change in principle, and have the problems of gear shifting, gear shifting and power interruption in the prior art; the transmission ratio range of the AMT is limited by gear setting and is applied to heavy vehicles, in order to expand the transmission ratio range, a large number of gears need to be set, the gear shifting process is slow, the operation is complex, and a lot of drivers of large vehicles are reluctant to step on the brake; the AMT gear shifting process depends on a complex control strategy, so that the accurate gear shifting time is difficult to master, and the problems of high energy consumption and low efficiency exist; the AMT transmission has the disadvantages of complex structure, high manufacturing cost and difficult maintenance.
Disclosure of Invention
The invention aims to solve the problems and designs a single-side input and output three-planetary-row stepless speed change mechanism and a speed change method thereof.
The technical scheme of the invention is that the single-side input and output three-planet-row stepless speed change mechanism comprises a first planet row, a second planet row and a third planet row, wherein a first gear ring on the first planet row is connected with a second planet carrier on the second planet row, the second planet carrier on the second planet row is connected with a third sun gear on the third planet row through a connecting shaft, a first planet carrier on the first planet row is connected with a second gear ring on the second planet row and a third gear ring on the third planet row, a connecting body of the first planet carrier, the second gear ring and the third gear ring is provided with a one-way stopper, a third planet carrier on the third planet row is connected with an output component, and a second input shaft connected with a second sun gear on the second planet row penetrates through the second planet carrier, The connecting shaft, the third sun gear, the third planet carrier and the output part are connected with a second driving piece, and a first input shaft connected with the first sun gear on the first planet row penetrates through the second sun gear, the second input shaft and the second driving piece to be connected with the first driving piece.
As a further explanation of the present invention, the external teeth of the first sun gear engage with a first planet gear, the first planet gear is mounted on the first planet carrier, and the first planet gear engages with the inner ring teeth of the first ring gear;
the outer teeth of the second sun gear are meshed with a second planet gear, the second planet gear is arranged on the second planet carrier, and the second planet gear is meshed with the inner ring teeth of the second gear ring;
and the outer teeth of the third sun gear are engaged with a third planet gear, the third planet gear is arranged on the third planet carrier, and the third planet gear is engaged with the inner ring teeth of the third gear ring.
As a further explanation of the present invention, the one-way stopper serves to limit the rotational directions of the first carrier, the second ring gear, and the third ring gear, and the one-way stopper makes the rotational directions of the first carrier, the second ring gear, and the third ring gear coincide with only the steering of the second driver.
The invention also provides a speed change method of the three-planet-row stepless speed change mechanism based on unilateral input and output, wherein a first driving piece and a first sun gear are connected through a first input shaft, so that the rotating speed of the first driving piece is the same as that of the first sun gear; the second driving piece and the second sun gear are connected through a second input shaft, so that the rotating speed of the second driving piece is the same as that of the second sun gear; the first planet carrier, the second gear ring and the third gear ring are connected, so that the rotating speeds of the first planet carrier, the second gear ring and the third gear ring are the same; the first gear ring, the second planet carrier and the third sun gear are connected, so that the rotating speeds of the first gear ring, the second planet carrier and the third sun gear are the same; the output part is connected with the third planet carrier, so that the rotating speeds of the third planet carrier and the output part are the same; the stepless continuous change of the rotating speed of the output part is realized by adjusting and controlling the rotating speed of the first driving part and the rotating speed of the second driving part, and the speed ratio is correspondingly changed in the process.
As a further explanation of the invention, it is assumed that: the rotating speed of the first driving part and the rotating speed of the first sun gear are N1The rotating speed of the second driving piece and the rotating speed of the second sun wheel are N2The rotation speed of the first gear ring, the second planet carrier and the third sun gear is N3The rotation speed of the first planet carrier, the second gear ring and the third gear ring is N4The third planet carrier and the output member rotate at a speed N5The number of teeth of the first sun gear is Z1The number of teeth of the first gear ring is Z2The number of teeth of the second sun gear is Z3The number of teeth of the second gear ring is Z4The number of teeth of the third sun gear is Z5The number of teeth of the third gear ring is Z6When said N is1、N2、N3、N4And N5When any two numerical values in the vector diagram are determined, the other three numerical values can be obtained through proportional relation calculation of line segments in the vector diagram; controlling the speed N of the first drive member by regulation1And the rotational speed N of the second drive member2The rotational speed N of the output member can be realized5Continuous stepless variation of (2); controlling the speed N of the first drive member by regulation1And the rotational speed N of the second drive member2The output states of the output means are made to include state a, state B, state C, state D, and state E.
As a further elaboration of the invention, in state a the rotational speed N of the first drive element is1Is reversed, the rotational speed N of the second drive member2Is in the forward direction, the rotational speed N of the second drive member2And the rotational speed N of the first drive member1Is equal to [ Z ]1×(Z3+Z4)]/(Z2×Z3) A rotation speed N of the first carrier, the second ring gear and the third ring gear4Is 0, the rotational speed N of the output member5The direction of rotation of (c) is the forward direction.
As a further elaboration of the invention, in state B the rotational speed N of the first drive element is1Is reversed, of said second drive memberRotational speed N2Is in the forward direction, the rotational speed N of the second drive member2And the rotational speed N of the first drive member1Is greater than [ Z ]1×(Z3+Z4)]/(Z2×Z3) A rotation speed N of the first carrier, the second ring gear and the third ring gear4The direction of rotation being in the forward direction, the speed of rotation N of the output member5The direction of rotation of (c) is the forward direction.
As a further elaboration of the invention, in state C the rotational speed N of the first drive element1Is reversed, the rotational speed N of the second drive member2Is in the forward direction, the rotational speed N of the second drive member2And the rotational speed N of the first drive member1Is less than [ Z ]1×(Z3+Z4)]/(Z2×Z3) A rotation speed N of the first carrier, the second ring gear and the third ring gear4Is reversed, the rotational speed N of the output member5May be forward or reverse, and in order to prevent this, a one-way stopper is provided on the connecting body of the first carrier, the second ring gear and the third ring gear to limit the rotational speed N of the first carrier, the second ring gear and the third ring gear4The rotation direction of the output component can only be a forward direction and can not be a reverse direction, so that the rotation speed N of the output component is ensured5The direction of turning of (1) is always positive.
As a further elaboration of the invention, in state D the rotational speed N of the first drive element1Is 0, the rotational speed N of the second driving member2Is a forward direction, the rotational speed N of the first carrier, the second ring gear and the third ring gear4Is a forward direction, the rotational speed N of the output member5The direction of rotation of (c) is the forward direction.
As a further elaboration of the invention, in state E the rotational speed N of the first drive element is1And the rotational speed N of the second drive member2Are the same in size, the steering is forward, and the rotating speeds N of the first planet carrier, the second gear ring and the third gear ring are positive4And said N1And said N2Same size, turnThe directions are all positive, and the rotating speed N of the output part5And said N1、N2And N4Is the same, the steering is positive, and the transmission ratio of the state E is 1.
As a further explanation of the invention, the rotational speed of the second drive member is N when the first drive member fails2The rotation speed N of the first carrier, the second ring gear and the third ring gear is in the forward direction4There is a tendency of reverse rotation, in which a one-way stopper limits reverse rotation thereof to a rotational speed N of the first carrier, the second ring gear and the third ring gear4Is 0, the rotational speed N of the output member5The power of the second driving piece is output through the second planet row and the third planet row in a speed reduction and torque increase mode in a positive direction, and the transmission ratio is [ (Z)3+Z4)×(Z5+Z6)]/(Z3×Z5)。
As a further explanation of the invention, the rotational speed of the first drive member is N when the second drive member fails1In the reverse direction, the rotational speed N of the first carrier, the second ring gear and the third ring gear4There is a tendency of reverse rotation, in which a one-way stopper limits the reverse rotation to a rotational speed N of the first carrier, the second ring gear and the third ring gear4Is 0, the rotational speed N of the output member5The power of the first driving piece is output through the first planet row and the third planet row in a speed reduction and torque increase mode in a positive rotation mode, and the transmission ratio is [ (Z)3+Z4)×(Z5+Z6)]/(Z3×Z5)。
The invention provides a unilateral input and output three-planet-row stepless speed change mechanism and a speed change method thereof, which change the transmission ratio between an input end and an output end by adjusting the rotating speeds of a first driving piece and a second driving piece and matching the first planet row, the second planet row, a third planet row and a one-way retainer, thereby realizing the stepless speed change of the output end. In addition, all set up the link of first driving piece, second driving piece and output unit in this infinitely variable speed mechanism's one end, make the input and the output of power all be in infinitely variable speed mechanism's one end, and first input shaft passes second input shaft and second driving piece and is connected with first driving piece, and the utilization ratio in promotion space that such design can be very big makes whole power equipment more reasonable in arranging and space utilization.
Drawings
FIG. 1 is a schematic diagram of a single-side input and output three-planetary-row continuously variable transmission mechanism according to an embodiment of the present invention;
FIG. 2 is a speed vector diagram for a first planetary gear set in accordance with an embodiment of the present invention;
FIG. 3 is a speed vector diagram for a second planetary row as provided by an embodiment of the present invention;
FIG. 4 is a third planetary row tachometric vector diagram provided in accordance with an embodiment of the present invention;
FIG. 5 is a rotation speed vector diagram provided by the embodiment of the present invention and combining FIG. 2, FIG. 3 and FIG. 4;
FIG. 6 shows the rotational speeds N of the first carrier, the second ring gear and the third ring gear according to the embodiment of the present invention4A rotation speed vector diagram when the rotation speed vector diagram is 0;
FIG. 7 shows the rotational speeds N of the first carrier, the second ring gear and the third ring gear according to the embodiment of the present invention4A rotation speed vector diagram when less than 0;
FIG. 8 shows the first driver speed N according to an embodiment of the present invention1A rotation speed vector diagram when the rotation speed vector diagram is 0;
FIG. 9 is a speed vector diagram illustrating the same speed of the first and second drivers provided by an embodiment of the present invention;
FIG. 10 shows the rotational speed N of the first and second drivers according to an embodiment of the present invention1And N2The steering is a rotating speed vector diagram in the positive direction at the same time;
FIG. 11 shows the rotational speeds N of the first carrier, the second ring gear and the third ring gear under the reverse operating condition provided by the embodiment of the invention4A rotation speed vector diagram when the rotation speed vector diagram is 0;
FIG. 12 shows an embodiment of the present inventionThe rotating speed N of the first planet carrier, the second gear ring and the third gear ring under the condition of reversing is provided4A rotation speed vector diagram when less than 0;
FIG. 13 shows the rotational speed N of the second driving member when the first driving member fails according to an embodiment of the present invention2The steering of (1) is a rotating speed vector diagram when the steering is positive;
FIG. 14 shows the rotational speed N of the first driving member when the second driving member fails according to an embodiment of the present invention1Is a rotation speed vector diagram in the reverse direction.
Reference numerals:
1-first planet row, 101-first sun gear, 102-first planet carrier, 103-first ring gear, 2-second planet row, 201-second sun gear, 202-second planet carrier, 203-second ring gear, 3-third planet row, 301-third sun gear, 302-third planet carrier, 303-third ring gear, 4-one-way stopper, 5-first input shaft, 6-second input shaft, 7-connecting shaft; 8-output component.
Detailed Description
Firstly, the purpose of the embodiment of the invention is explained, and the problem that the AMT has gear shifting pause and power interruption in the nature is solved; the transmission ratio range of the AMT is limited by gear setting and is applied to heavy vehicles, in order to expand the transmission ratio range, a large number of gears need to be set, the gear shifting process is slow, the operation is complex, and a lot of drivers of large vehicles are reluctant to step on the brake; the AMT gear shifting process depends on a complex control strategy, so that the accurate gear shifting time is difficult to master, and the problems of high energy consumption and low efficiency exist; the AMT has the existing problems of complex structure, high manufacturing cost, difficult maintenance and the like, so a single-side input and output three-planetary-row stepless speed change mechanism is provided to solve the existing problems.
The following describes embodiments of the present invention with reference to the accompanying drawings, and first introduces specific structures of the embodiments of the present invention.
Referring to fig. 1, a single-side input and output three-planetary-row continuously variable transmission mechanism comprises a first planetary row 1, a second planetary row 2 and a third planetary row 3, wherein a first ring gear 103 on the first planetary row 1 is connected with a second planet carrier 202 on the second planetary row 2, the second planet carrier 202 on the second planetary row 2 is connected with a third sun gear 301 on the third planetary row 3 through a connecting shaft 7, a first planet carrier 102 on the first planetary row 1 is connected with a second ring gear 203 on the second planetary row 2 and a third ring gear 303 on the third planetary row 3, a one-way stopper 4 is arranged on a connecting body of the first planet carrier 102, the second ring gear 203 and the third ring gear 303, a third planet carrier 302 on the third planetary row 3 is connected with an output component 8, a first sun gear 101 on the first planetary row 1 is connected with a first driving component through a first input shaft 5, a second input shaft 6 connected with a second sun gear 201 on the second planetary row 2 penetrates through the second planet carrier 202, The connecting shaft 7, the third sun gear 301, the third planet carrier 302 and the output member 8 are connected to a second drive element, and the first input shaft 5 connected to the first sun gear 101 on the first planetary row 1 is connected to the first drive element via the second sun gear 201 and the second input shaft 6.
Referring to fig. 1, a first sun gear 101 is engaged with first planet gears on outer teeth, the first planet gears are mounted on a first planet carrier 102, and the first planet gears are engaged with inner ring teeth of a first ring gear 103; a second planet wheel is meshed with the outer teeth of the second sun gear 201, is arranged on a second planet carrier 202, and is meshed with the inner ring teeth of a second ring gear 203; the third sun gear 301 is engaged with third planetary gears on its outer teeth, which are mounted on a third carrier 302, and engaged with inner ring teeth of a third ring gear 303.
Referring to fig. 1, the one-way stopper 4 serves to limit the rotational direction of the first carrier 102, the second ring gear 203 and the third ring gear 303, and the one-way stopper 4 makes the rotational direction of the first carrier 102, the second ring gear 203 and the third ring gear 303 coincide with only the steering of the second driver.
In the following, we need to describe a speed change method of a three-planetary-row continuously variable transmission mechanism based on single-side input and output in combination with the specific structure of the embodiment of the present invention.
According to the basic principle of the planetary gear, the rotating speeds of three members, namely a sun gear, a ring gear and a planet carrier, of any two members are determined, the rotating speed of the other member is also determined, and the rotating speed relations of the members are in corresponding proportion according to the number of teeth of the sun gear and the number of teeth of the ring gear.
According to the basic principle of the planetary gear, the rotation speed of any two of the three components, namely the sun gear, the ring gear and the planet carrier, is the same, and the rotation speed of the other component is also the same.
Therefore, the rotational speed of the first driving member is the same as the rotational speed of the first sun gear 101, and is set to N1(ii) a The rotational speed of the second driving member is the same as the rotational speed of the second sun gear 201, and is set to N2(ii) a The rotation speeds of the first ring gear 103, the second carrier 202, and the third sun gear 301 are the same, and N is set3(ii) a The rotation speeds of the first carrier 102, the second ring gear 203, and the third ring gear 303 are the same, and are set to N4(ii) a The third carrier 302 and the output member 8 have the same rotational speed, and are set to N5(ii) a The number of teeth of the first sun gear 101 is set to Z1The number of teeth of the first ring gear 103 is Z2The number of teeth of the second sun gear 201 is Z3The number of teeth of the second ring gear 203 is Z4The number of teeth of the third sun gear 301 is Z5The number of teeth of the third ring gear 303 is Z6。
A rotation speed vector diagram of the first planetary row 1 is obtained according to a rotation speed vector calculation method of the planetary gear, as shown in fig. 2. N is a radical of1Is the rotational speed of the first sun gear 101, N3Is the rotational speed of the first ring gear 103, N4Is the rotational speed of the first carrier 102. N is a radical of1、N3、N4The length of (d) represents the magnitude of the rotation speed, the arrow direction represents the rotation speed direction, the arrow direction represents the rotation speed as a forward direction, and the arrow direction represents the rotation speed as a reverse direction. Set L2/L3＝Z1/Z2。
A rotation speed vector diagram of the second planetary line 2 is obtained according to a rotation speed vector calculation method of the planetary gears, as shown in fig. 3. N is a radical of2Is the rotational speed, N, of the second sun gear 2014Is the rotational speed, N, of the second ring gear 2033Is the rotational speed of the second carrier 202. N is a radical of2、N3、N4The length of (d) represents the magnitude of the rotation speed, the arrow direction represents the rotation speed direction, the arrow direction represents the rotation speed as a forward direction, and the arrow direction represents the rotation speed as a reverse direction. Set L2/L1＝Z3/Z4。
A rotation speed vector diagram of the third planetary row 3 is obtained according to the rotation speed vector calculation method of the planetary gears, as shown in fig. 4. N is a radical of3Is the rotational speed of the third sun gear 301, N4Is the rotational speed of the third ring gear 303, N5Is the rotational speed of the third carrier 302. N is a radical of3、N4、N5The length of (d) represents the magnitude of the rotation speed, the arrow direction represents the rotation speed direction, the arrow direction represents the rotation speed as a forward direction, and the arrow direction represents the rotation speed as a reverse direction. Set L5/L4＝Z5/Z6。
In FIGS. 2, 3 and 4, L1、L2、L3、L4、L5Only the corresponding proportional relationship needs to be satisfied, L1、L2、L3、L4、L5Does not affect the calculation of N1、N2、N3、N4、N5The size of (2). FIG. 5 can be obtained by combining FIG. 2, FIG. 3 and FIG. 4, let L2＝L4+L5。
See FIG. 5, N1Is the rotational speed of the first sun gear 101, i.e. the rotational speed of the first drive member; n is a radical of2Is the rotational speed of the second sun gear 201, i.e., the rotational speed of the second driving member; n is a radical of3Is the rotational speed of the first ring gear 103, the second carrier 202, and the third sun gear 301; n is a radical of4Is the rotational speed of the first carrier 102, the second ring gear 203 and the third ring gear 303; n is a radical of5Is the rotational speed of the third planet carrier 302 and the output member 8.
N1、N2、N3、N4And N5Any two values are determined, and the other three values can be calculated through the proportional relation of line segments in the vector diagram. I.e. the rotational speed N of the first drive member1Determining the rotational speed N of the second drive element2Determining the rotational speed N of the output member 85And is also uniquely determined. Controlling the speed N of the first drive member by regulation1And the rotational speed N of the second drive member2The rotational speed N of the output member 8 can be realized5Continuously stepless variation of (a).
The speed change principle of the single-side input and output three-planetary-row stepless speed change mechanism according to the embodiment of the invention is described below by combining specific working conditions.
1. Starting condition
Referring to fig. 5 and 6, the rotational speed N of the first drive member at take-off1Is reversed, the rotational speed N of the second drive member2The direction of rotation of (c) is the forward direction. The two driving parts are started and accelerated at the same time by controlling the rotating speed N of the second driving part2And the rotational speed N of the first drive member1Is always greater than (as in FIG. 5) or equal to (as in FIG. 6) [ Z ]1×(Z3+Z4)]/(Z2×Z3) Control of the rotational speed N of the output member 8 can be achieved5The acceleration is gradually increased from 0, and the direction is changed to the positive direction. Under the working condition, the transmission ratio is maximum, the power of the first driving piece and the power of the second driving piece are coupled together, and the vehicle is decelerated and torque-increased to output, so that the vehicle can accelerate to move forwards.
2. Acceleration and deceleration conditions
The acceleration and deceleration may be in accordance with the speed N of the first drive member1The steering is divided into three cases, which specifically comprise:
1) situation one
Referring to fig. 5 and 6, the rotational speed N of the first driver1Is reversed, the rotational speed N of the second drive member2The direction of rotation of (c) is the forward direction. Rotational speed N of the second drive member2And the rotational speed N of the first drive member1Always greater than or equal to [ Z ]1×(Z3+Z4)]/(Z2×Z3). By controlling the speed N of the first drive member1And the rotational speed N of the second drive member2By increasing or decreasing the speed, the rotational speed N of the output member 8 can be controlled5The steering direction is the forward direction, so that the vehicle can accelerate or decelerate to run forwards.
2) Situation two
Referring to FIG. 8, the rotational speed N of the first driver1Is gradually reduced to 0, the rotating speed N of the second driving part2The direction of rotation is forward, by controlling the speed of rotation N of the first drive member1Is 0 and the rotational speed N of the second driving member2The speed of the increase and decrease of the speed,can realize the output rotating speed N5The steering direction is the forward direction, so that the vehicle can accelerate or decelerate to run forwards.
3) Situation three
Referring to FIG. 10, the rotational speed N of the first driver1Is in the forward direction, the rotational speed N of the second drive member2The direction of rotation of (c) is the forward direction. By controlling the speed N of the first drive member1And the rotational speed N of the second drive member2The speed of increase and decrease of the speed can realize the output rotating speed N5The steering direction is the forward direction, so that the vehicle can accelerate or decelerate to run forwards.
Alternatively, the method of acceleration and deceleration may be adjusted by maintaining the speed N of the first drive member1Without change, by adjusting the speed N of the second drive member2To adjust the rotational speed N of the output member 85The size of (d); the rotating speed N of the second driving member can be maintained2Without change, by adjusting the speed N of the first drive member1To adjust the rotational speed N of the output member 85The size of (2). When the speed N of the output member 8 is achieved5In the process of acceleration or deceleration, the first driving part and the second driving part can be different according to respective efficient working areas, and the control system controls the acceleration, deceleration and rotation speed maintenance of the first driving part and the second driving part according to the current working condition. Therefore, the first driving part and the second driving part can work in respective high-efficiency working areas for a long time, and the energy-saving effect is achieved.
3. Maximum vehicle speed condition
Referring to fig. 9 and 10, the rotational speed N of the first driver1Is in the forward direction, the rotational speed N of the second drive member2The direction of rotation of (c) is the forward direction. When the rotating speed N of the first driving member1And the rotational speed N of the second drive member2The rotational speed N of the output member 8 when all reach the maximum rotational speed5The maximum speed is also reached, at which time the vehicle speed reaches the maximum vehicle speed. If the rotating speed N of the first driving member1And the rotational speed N of the second drive member2Is the same, the rotational speed N of the output member 8 is then5The maximum rotational speed that can be achieved and the maximum rotation of the first and second drive membersSpeed N1、N2Also, the gear ratio is 1.
Aiming at the starting working condition and the acceleration and deceleration working condition, a dangerous working condition needs to be considered to avoid.
Example (c): referring to FIG. 7, when the first driving member rotates at a speed N1Is reversed, the rotational speed N of the second drive member2The steering direction of the first driving part and the second driving part is positive, and when the vehicle runs in a starting stage or a middle and low speed stage, if the control of the rotating speeds of the first driving part and the second driving part is inaccurate or fails, the rotating speed N of the second driving part occurs2And the rotational speed N of the first drive member1Is less than [ Z ]1×(Z3+Z4)]/(Z2×Z3) At this time, as shown in FIG. 7, the rotational speed N of the output member 85The steering of the vehicle can be in a reverse direction, and the vehicle can suddenly run backwards, so that serious accidents are easy to happen. To prevent this from happening, limiting the speed of rotation N of the first planet carrier 102, the second ring gear 203 and the third ring gear 303 is achieved by providing a one-way stop 4 on the connection body of the first planet carrier 102, the second ring gear 203 and the third ring gear 3034The direction of rotation of (1) can only be a forward direction, but cannot be a reverse direction. This ensures the rotational speed N of the output member 85The direction of turning of (1) is always positive. Therefore, when the dangerous condition occurs, the rotation speed N of the first carrier 102, the second ring gear 203 and the third ring gear 303 is limited due to the one-way stopper 44The steering can only be in a forward direction and can not be in a reverse direction, at the moment, the two driving pieces can be mutually dragged, and the rotating speed N of the second driving piece2And the rotational speed N of the first drive member1Will always be equal to [ Z ]1×(Z3+Z4)]/(Z2×Z3) Rotational speed N of the first carrier 102, the second ring gear 203, and the third ring gear 3034Equal to 0, rotational speed N of the output member 85The steering of (2) can only be in the forward direction, so that the reverse driving cannot happen suddenly.
4. Working condition of backing car
Referring to fig. 11 and 12, the rotational speed N of the first driving member when reversing1Is in the forward direction, the rotational speed N of the second drive member2The direction of rotation of (1) is reversed. Two driving membersStarting acceleration at the same time by controlling the speed N of the second drive member2And the rotational speed N of the first drive member1Is always greater than (as in FIG. 12) or equal to (as in FIG. 11) [ Z ]1×(Z3+Z4)]/(Z2×Z3) Control of the rotational speed N of the output member 8 can be achieved5Gradually accelerate from 0 and turn to reverse. If the control of the rotating speeds of the first driving part and the second driving part is inaccurate or fails, the rotating speed N of the second driving part occurs2And the rotational speed N of the first drive member1Is less than [ Z ]1×(Z3+Z4)]/(Z2×Z3) The rotational speed N of the output member 85The steering may be in a forward direction, and at this time, the vehicle suddenly runs forward, so that a serious accident is easy to happen. To prevent this from happening, limiting the speed of rotation N of the first planet carrier 102, the second ring gear 203 and the third ring gear 303 is achieved by providing a one-way stop 4 on the connection body of the first planet carrier 102, the second ring gear 203 and the third ring gear 3034Can only be in reverse direction, but not in forward direction, thus ensuring the rotation speed N of the output member 85The direction of rotation of (c) is always reversed.
Except for the normal working condition and the dangerous working condition, some emergency working conditions need to be dealt with, and the embodiment of the invention takes the emergency working conditions into consideration and solves the problem.
Example (c): referring to FIG. 13, when the first driver fails, the second driver has a speed N2The rotation speed N of the first carrier 102, the second ring gear 203, and the third ring gear 303, which are steered in the forward direction4There is a tendency of reverse rotation in which the one-way stopper 4 restricts reverse rotation thereof to rotate the rotational speed N of the first carrier 102, the second ring gear 203 and the third ring gear 30340, rotational speed N of the output member 85The power of the second driving piece is output through the second planet row 2 and the third planet row 3 in a speed reduction and torque increase way with the transmission ratio of [ (Z)3+Z4)×(Z5+Z6)]/(Z3×Z5) So that the vehicle can continue to accelerate or decelerate forward.
Referring to FIG. 14, when the second driver fails, the first driver has a speed of N1Turning toIn the reverse direction, the rotational speed N of the first carrier 102, the second ring gear 203 and the third ring gear 3034There is a tendency of reverse rotation, in which the one-way stopper 4 restricts the reverse rotation to rotate the rotational speed N of the first carrier 102, the second ring gear 203, and the third ring gear 30340, rotational speed N of the output member 85The power of the first driving piece is output through the first planet row 1 and the third planet row 3 in a speed reduction and torque increase mode in the positive direction, and the transmission ratio is [ Z ]2×(Z5+Z6)]/(Z1×Z5) So that the vehicle can continue to accelerate or decelerate forward.
Therefore, when one driving part fails, the other driving part can still drive the vehicle to run, and although the dynamic property is reduced, the vehicle can run to a maintenance place or a safety place by means of the one driving part, so that the reliability of the vehicle can be greatly improved.
The unilateral input and output three-planet-row stepless speed change mechanism and the speed change method thereof provided by the embodiment of the invention have the following advantages:
1. the single-side input and output three-planet-row stepless speed change mechanism provided by the embodiment of the invention has no power interruption in the speed regulation process, runs quietly and stably, has better vehicle using experience when a user uses a vehicle, can greatly meet the requirements of customers in sense, and lays a good foundation for popularization and use of the product.
2. The unilateral input and output three-planet-row stepless speed change mechanism can realize that the output end has large torque from low speed to high speed, and the large torque is output to realize that the vehicle has the capability of quick acceleration starting when driving, and the large torque can climb larger gradient when climbing the slope, and the large torque can also meet the requirement of more people, so that the audience area of the product is larger.
3. The single-side input and output three-planet-row stepless speed change mechanism can realize stepless continuous change of output rotating speed, the driving piece at the input end can work in a high-efficiency interval for a long time, the working efficiency is improved, the effect of saving more energy can be achieved in the aspect of energy use, and more contributions can be made in the aspect of energy saving.
4. The unilateral input and output three-planet-row stepless speed change mechanism has simple and convenient speed regulation, and can realize stepless continuous change of output rotating speed only by controlling the rotating speeds of the first driving piece and the second driving piece, thereby reducing the requirement of vehicles on a control system, widening the popularization and application range of the product and ensuring the popularization and popularity of the product to a certain extent.
5. According to the embodiment of the invention, the power of the first driving part and the power of the second driving part are coupled together to drive the vehicle to run, when one driving part fails, the other driving part can still continue to drive the vehicle to run, so that when a vehicle owner uses the vehicle, even if one driving part fails, the vehicle owner can drive the vehicle by the other driving part and drive the vehicle to a maintenance place in time, the occurrence of a trailer calling event is avoided, and the vehicle using experience of the vehicle owner is better taken care of.
6. Compared with the traditional driving mode of a single driving part, the product provided by the embodiment of the invention not only can be driven by adopting the double driving parts, but also can be matched with the driving part with smaller volume and lower rotating speed, the driving part with small volume is more beneficial to the arrangement design of the driving part in the vehicle body, the aesthetic design of the appearance of the vehicle body at the later stage is more convenient, and the cost can be saved by using the smaller driving part.
7. The unilateral input and output three-planetary-row stepless speed change mechanism has high transmission rate, a motor with lower power and lower rotating speed can be selected as a driving piece under the same working condition, and compared with a high-power battery, the low-power battery can better prevent the battery from overheating, and the use safety of the battery is indirectly improved through the embodiment of the invention.
8. The single-side input and output three-planetary-row stepless speed change mechanism adopts three-planetary-row transmission, increases the transmission ratio, further increases the torque, can be applied to heavy trucks such as trucks, muck trucks and buses with larger loads, and further widens the application range of the embodiment of the invention.
9. According to the unilateral input and output three-planet-row stepless speed change mechanism, the connecting ends of the first driving piece, the second driving piece and the output part 8 are all arranged at one end of the stepless speed change mechanism, so that power is input and output at one end of the stepless speed change mechanism, and the first input shaft 5 penetrates through the second input shaft 6 and the second driving piece to be connected with the first driving piece.
The technical solutions described above only represent the preferred technical solutions of the present invention, and some possible modifications to some parts of the technical solutions by those skilled in the art all represent the principles of the present invention, and fall within the protection scope of the present invention.
Claims (12)
1. A single-side input and output three-planet-row continuously variable transmission mechanism is characterized by comprising a first planet row (1), a second planet row (2) and a third planet row (3), wherein a first gear ring (103) on the first planet row (1) is connected with a second planet carrier (202) on the second planet row (2), the second planet carrier (202) on the second planet row (2) is connected with a third sun gear (301) on the third planet row (3) through a connecting shaft (7), a first planet carrier (102) on the first planet row (1) is connected with a second gear ring (203) on the second planet row (2) and a third gear ring (303) on the third planet row (3), and a one-way retainer (4) is arranged on a connecting body of the first planet carrier (102), the second gear ring (203) and the third gear ring (303), a third planet carrier (302) on the third planet row (3) is connected with an output part (8), a second input shaft (6) connected with a second sun gear (201) on the second planet row (2) penetrates through the second planet carrier (202), the connecting shaft (7), the third sun gear (301), the third planet carrier (302) and the output part (8) are connected with a second driving part, and a first input shaft (5) connected with a first sun gear (101) on the first planet row (1) penetrates through the second sun gear (201), the second input shaft (6) and the second driving part to be connected with the first driving part.
2. A single-sided input, output three planetary gear set continuously variable transmission according to claim 1, characterized in that the first sun gear (101) is meshed with a first planet gear on its outer teeth, which is mounted on the first carrier (102), and which is meshed with the inner ring teeth of the first ring gear (103);
the second sun gear (201) is meshed with a second planet gear on external teeth, the second planet gear is arranged on the second planet carrier (202), and the second planet gear is meshed with internal ring teeth of the second ring gear (203);
and a third planet wheel is meshed with the external teeth of the third sun gear (301), is arranged on the third planet carrier (302), and is meshed with the inner ring teeth of the third gear ring (303).
3. The single-input, single-output triple planetary gear set stepless speed change mechanism according to claim 1, is characterized in that the one-way stopper (4) is used for limiting the rotation direction of the first carrier (102), the second ring gear (203) and the third ring gear (303), and the one-way stopper (4) makes the rotation direction of the first carrier (102), the second ring gear (203) and the third ring gear (303) consistent with the steering of the second driving piece only.
4. A speed change method of a three-planetary-row stepless speed change mechanism based on single-side input and output is characterized in that a first driving piece and a first sun gear (101) are connected through a first input shaft (5), so that the rotating speed of the first driving piece is the same as that of the first sun gear (101); the second driving piece and the second sun gear (201) are connected through a second input shaft (6), so that the rotating speed of the second driving piece is the same as that of the second sun gear (201); the first planet carrier (102), the second gear ring (203) and the third gear ring (303) are connected, so that the rotating speeds of the first planet carrier (102), the second gear ring (203) and the third gear ring (303) are the same; a first gear ring (103), a second planet carrier (202) and a third sun gear (301) are connected, so that the rotation speeds of the first gear ring (103), the second planet carrier (202) and the third sun gear (301) are the same; the output part (8) is connected with the third planet carrier (302) so that the rotating speeds of the third planet carrier (302) and the output part (8) are the same; by controlling the rotational speed of the first drive element and the rotational speed of the second drive element in a regulated manner, a continuously variable change of the rotational speed of the output element (8) is achieved, in which process the speed ratio is also correspondingly changed.
5. The method for shifting a three planetary gear set continuously variable transmission mechanism according to claim 4, wherein the following are set: the rotational speed of the first driving member and the rotational speed of the first sun gear (101) are N1The rotation speed of the second driving piece and the rotation speed of the second sun wheel (201) are N2The rotation speed of the first gear ring (103), the second planet carrier (202) and the third sun gear (301) is N3The rotational speeds of the first carrier (102), the second ring gear (203) and the third ring gear (303) are N4The third planet carrier (302) and the output member (8) have a rotational speed N5The number of teeth of the first sun gear (101) is Z1The number of teeth of the first ring gear (103) is Z2The number of teeth of the second sun gear (201) is Z3The number of teeth of the second ring gear (203) is Z4The number of teeth of the third sun gear (301) is Z5The number of teeth of the third gear ring (303) is Z6When said N is1、N2、N3、N4And N5When any two values are determined, the other three values can be calculated through the proportional relation of line segments in the vector diagram; controlling the speed N of the first drive member by regulation1And the rotational speed N of the second drive member2The rotational speed N of the output member (8) can be realized5Continuous stepless variation of (2); controlling the speed N of the first drive member by regulation1And the rotational speed N of the second drive member2The output state of the output member (8) is made to include a state A, a state B, a state C, a state D and a state E.
6. The single-input/output-based speed change method for a three planetary gear set continuously variable transmission mechanism according to claim 5, wherein in the state A, the rotating speed N of the first driving member1Is reversed, the rotational speed N of the second drive member2Is in the forward direction, the rotational speed N of the second drive member2And the rotational speed N of the first drive member1Is equal to [ Z ]1×(Z3+Z4)]/(Z2×Z3) A rotational speed N of the first carrier (102), the second ring gear (203) and the third ring gear (303)4Is 0, the rotational speed N of the output member (8)5The direction of rotation of (c) is the forward direction.
7. The single-input/output-based speed change method for a three planetary gear set continuously variable transmission mechanism according to claim 5, wherein in the state B, the rotating speed N of the first driving member is1Is reversed, the rotational speed N of the second drive member2Is in the forward direction, the rotational speed N of the second drive member2And the rotational speed N of the first drive member1Is greater than [ Z ]1×(Z3+Z4)]/(Z2×Z3) A rotational speed N of the first carrier (102), the second ring gear (203) and the third ring gear (303)4Is a forward direction, the rotational speed N of the output member (8)5The direction of rotation of (c) is the forward direction.
8. A method as claimed in claim 5, wherein in state C, the speed N of the first drive member is N1Is reversed, the rotational speed N of the second drive member2Is in the forward direction, the rotational speed N of the second drive member2The ratio of the rotational speed N1 of the first driving member to the rotational speed N1 of the first driving member is less than [ Z1×(Z3+Z4)]/(Z2×Z3) A rotational speed N of the first carrier (102), the second ring gear (203) and the third ring gear (303)4Is reversed, said output means (8) Rotational speed N of5In order to prevent the situation from happening, a one-way stopper (4) is arranged on a connecting body of the first planet carrier (102), the second gear ring (203) and the third gear ring (303) to limit the rotating speed N of the first planet carrier (102), the second gear ring (203) and the third gear ring (303)4Can only be in the forward direction but not in the reverse direction, thus ensuring the rotating speed N of the output component (8)5The direction of turning of (1) is always positive.
9. A method as claimed in claim 5, wherein in state D, the speed N of the first drive member is N1Is 0, the rotational speed N of the second driving member2Is a forward direction, the rotational speed N of the first carrier (102), the second ring gear (203) and the third ring gear (303)4Is a forward direction, the rotational speed N of the output member (8)5The direction of rotation of (c) is the forward direction.
10. A method as claimed in claim 5, wherein in state E, the speed N of the first drive member is N1And the rotational speed N of the second drive member2Are all in a forward direction, and the rotational speeds N of the first carrier (102), the second ring gear (203) and the third ring gear (303)4And said N1And said N2The same size, the rotation directions are positive, and the rotating speed N of the output part (8)5And said N1、N2And N4Is the same, the steering is positive, and the transmission ratio of the state E is 1.
11. The single-input-output-based speed change method for the three-planetary-row continuously variable transmission mechanism according to claim 5, wherein when the first driving element fails, the rotation speed of the second driving element is N2Steering in the forward direction, the first carrier (102), the second ring gear (203) and the third ring gear (3)03) Rotational speed N of4The reverse rotation trend is existed, the reverse rotation of the first planet carrier (102), the second gear ring (203) and the third gear ring (303) is limited by a one-way stopper (4) at the time, and the rotating speed N of the first planet carrier, the second gear ring (203) and the third gear ring (303) is enabled to be4Is 0, the rotational speed N of the output member (8)5The power of the second driving piece is output through the second planet row (2) and the third planet row (3) in a speed reduction and torque increase way with the transmission ratio of [ (Z)3+Z4)×(Z5+Z6)]/(Z3×Z5)。
12. The single-input-output-based speed change method for the three-planetary-row continuously variable transmission mechanism according to claim 5, wherein when the second driving element fails, the rotating speed of the first driving element is N1In the opposite direction, the rotational speed N of the first carrier (102), the second ring gear (203) and the third ring gear (303)4The reverse rotation trend is existed, the reverse rotation of the first planet carrier (102), the second gear ring (203) and the third gear ring (303) is limited by a one-way stopper (4) at the time, and the rotating speed N of the first planet carrier, the second gear ring (203) and the third gear ring (303) is enabled to be4Is 0, the rotational speed N of the output member (8)5The power of the first driving piece is output through the first planetary row (1) and the third planetary row (3) in a speed reduction and torque increase mode in a transmission ratio of Z2×(Z5+Z6)]/(Z1×Z5)。
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