CN108386496B - Mechanical gear type stepless automatic speed variator - Google Patents
Mechanical gear type stepless automatic speed variator Download PDFInfo
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- CN108386496B CN108386496B CN201810426023.7A CN201810426023A CN108386496B CN 108386496 B CN108386496 B CN 108386496B CN 201810426023 A CN201810426023 A CN 201810426023A CN 108386496 B CN108386496 B CN 108386496B
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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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- 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
- F16H3/76—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion with an orbital gear having teeth formed or arranged for obtaining multiple gear ratios, e.g. nearly infinitely variable
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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
- F16H3/46—Gearings having only two central gears, connected by orbital gears
- F16H3/48—Gearings having only two central gears, connected by orbital gears with single orbital gears or pairs of rigidly-connected orbital gears
- F16H3/52—Gearings having only two central gears, connected by orbital gears with single orbital gears or pairs of rigidly-connected orbital gears comprising orbital spur gears
- F16H3/56—Gearings having only two central gears, connected by orbital gears with single orbital gears or pairs of rigidly-connected orbital gears comprising orbital spur gears both central gears being sun gears
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/02—Gearboxes; Mounting gearing therein
- F16H57/023—Mounting or installation of gears or shafts in the gearboxes, e.g. methods or means for assembly
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/02—Gearboxes; Mounting gearing therein
- F16H2057/02039—Gearboxes for particular applications
- F16H2057/02043—Gearboxes for particular applications for vehicle transmissions
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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
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/20—Transmissions using gears with orbital motion
- F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
- F16H2200/2007—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with two sets of orbital gears
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- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
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Abstract
The invention discloses a mechanical gear type stepless automatic transmission, which comprises an input shaft, an output shaft, a first planet row, a second planet row and a differential gear train, wherein the first planet row, the second planet row and the differential gear train are arranged in a shell, the input shaft is in meshing transmission with a gear ring of the first planet row, the second planet row and the first planet row share the gear ring and a planet carrier, the number of teeth of a second sun gear is larger than that of a first sun gear, the first sun gear transmits power to the differential gear train, the output shaft of the differential gear train is connected with a gear shifting assembly to transmit the power to the output shaft and is in transmission connection with a second sun gear, the second sun gear and the planet carrier can only rotate in one direction, the steering direction of the second sun gear is opposite to that of the gear ring, and. The invention realizes the stepless gear shifting of the transmission ratio through the first planet row, the second planet row and the differential gear train, has the continuity and smoothness of the prior CVT in the whole process, and has the characteristics of quick acceleration response and large torque bearing of the MT speed changer.
Description
Technical Field
The invention belongs to the technical field of transmission, and particularly relates to a mechanical gear type stepless automatic transmission.
Background
With the rapid development of the automobile industry, the related automobile parts industry is rapidly developed, along with the policy of the automobile industry, more and more people use the automobile, and the requirement on the driving comfort of the automobile is higher and higher, so that higher requirements are provided for the gear shifting quality of the transmission. There are four kinds of speed variator in real life, which are: the automatic transmission, the DCT dual clutch transmission and the CVT are controlled to change the transmission ratio through an electronic circuit system, so that the power loss of an engine is not as direct as that of the MT transmission when the engine is accelerated suddenly, and the engine has idle power loss.
Disclosure of Invention
The invention aims to overcome the defects of the prior art and provide a mechanical gear type stepless automatic transmission which has quick acceleration response, can bear large torque and has no pause and frustration.
In order to solve the technical problem, the mechanical gear type continuously variable automatic transmission provided by the invention comprises a first planet row arranged in a shell, wherein the first planet row comprises a first gear ring in meshing transmission with an input shaft, a plurality of first planet gears, a first planet carrier and a first sun gear, the first planet gears are rotatably arranged on the first planet carrier and are respectively and constantly meshed with the inner teeth of the first gear ring and the outer teeth of the first sun gear, the first sun gear transmits power to an output shaft, the mechanical gear type continuously variable automatic transmission also comprises a second planet row arranged in the shell, the second planet row comprises a second gear ring, a plurality of second planet gears, a second planet carrier and a second sun gear, the second planet gears are rotatably arranged on the second planet carrier and are respectively and constantly meshed with the inner teeth of the second gear ring and the outer teeth of the second sun gear, and the first gear ring and the second gear ring are the same gear ring, the first planet carrier and the second planet carrier are the same planet carrier, and the first sun gear is in transmission connection with the second sun gear through a gear.
Furthermore, the first sun gear can rotate automatically, the second sun gear is limited by a one-way bearing to rotate only in one direction, the rotation direction of the second sun gear is opposite to the rotation direction of the gear ring, the first planet carrier is limited by another one-way bearing to rotate only in one direction, the rotation direction of the first planet carrier is the same as or not rotating with the rotation direction of the gear ring, and the number of teeth of the first sun gear is smaller than that of the second sun gear.
The differential gear train comprises a driving side gear in transmission connection with the first sun gear, a driven side gear, a first gear and a second gear which are arranged side by side, a plurality of first bevel gears which are arranged on the first gear and are constantly meshed with the driving side gear and can rotate, a plurality of second bevel gears which are arranged on the second gear and can rotate, and a duplicate gear, wherein a double-sided side gear is arranged between the first gear and the second gear, one surface of the double-sided side gear is constantly meshed with the first bevel gear, the other surface of the double-sided side gear is constantly meshed with the second bevel gear, the duplicate gear is rotatably arranged in the shell and is constantly meshed with the first gear and the second gear respectively, the second bevel gear is constantly meshed with the driven side gear, and a third gear is coaxially and fixedly arranged on the driven side gear, the first sun gear is transmitted to the second sun gear and the output through a third gear and a gear.
Furthermore, the transmission ratio of power passing through the first bevel gear, the double-sided side gear and the second bevel gear from the driving side gear is different from the transmission ratio of power passing through the first bevel gear, the first gear, the duplicate gear, the second gear and the second bevel gear in sequence.
Furthermore, the third gear is in transmission connection with the second sun gear through a transmission mechanism, the transmission mechanism comprises a fourth gear in constant mesh with the third gear and a fifth gear in coaxial transmission connection with the fourth gear, a transmission shaft is coaxially and fixedly arranged on the second sun gear, a sixth gear is fixedly arranged on the transmission shaft, the third gear transmits power to the fifth gear sequentially through the fourth gear, and the fifth gear is in constant mesh with the sixth gear.
The gear shifting assembly comprises an external spline, an internal spline sliding sleeve, a first output gear and a second output gear, wherein the external spline is coaxially and fixedly connected to the output shaft; the fifth gear is in constant mesh with the first output gear, a seventh gear is fixedly arranged on the transmission shaft and is in constant mesh with the second output gear, and when the internal spline sliding sleeve is combined with the first output gear, the external spline drives the output shaft to be positively changed into a forward gear; when the internal spline sliding sleeve is combined with the second output gear, the external spline drives the output shaft to reversely rotate to reverse gear.
Furthermore, the axis of the first bevel gear is perpendicular to the axis of the first gear, and the axis of the second bevel gear is perpendicular to the axis of the second gear.
Further, the driving side gear is in coaxial transmission connection with the first sun gear.
Further, the input shaft and the output shaft are sleeved on the shell.
According to the mechanical gear type stepless automatic transmission in the technical scheme, the input shaft is fixedly connected with the first input gear, and the first gear ring is externally sleeved and fixed with the second input gear which is normally meshed with the first input gear.
A mechanical gear type stepless automatic speed changer comprises a shell, an input shaft and an output shaft which are sleeved on the shell, and further comprises a first planet row, a second planet row and a differential gear train which are arranged in the shell, wherein the first planet row comprises a first gear ring, a plurality of first planet wheels, a first planet carrier and a first sun gear which are in meshing transmission with the input shaft, the first planet wheels can be arranged on the first planet carrier in a self-rotating mode and are respectively and normally meshed with inner teeth of the first gear ring and outer teeth of the first sun gear, the second planet row comprises a second gear ring, a plurality of second planet wheels, a second planet carrier and a second sun gear, the second planet wheels can be arranged on the second planet carrier in a self-rotating mode and are respectively and normally meshed with inner teeth of the second gear ring and outer teeth of the second sun gear, the first gear ring and the second gear ring are the same gear ring, and the first planet carrier and the second planet carrier are the same planet carrier, the first sun gear can rotate automatically, the second sun gear is limited by a one-way bearing to rotate only in one direction, and the rotation direction of the second sun gear is opposite to or not rotating with the rotation direction of the gear ring;
the differential gear train comprises a driving side gear, a driven side gear, a first gear, a second gear, a plurality of first bevel gears, a plurality of second bevel gears and a duplicate gear, wherein the driving side gear is coaxially connected with the first sun gear in a transmission manner, the first gear and the second gear are arranged side by side, the first bevel gears are arranged on the first gear, are constantly meshed with the driving side gear and can rotate, the second bevel gears are arranged on the second gear, are respectively and constantly meshed with the second gear, the axis of the first bevel gear is vertical to the axis of the first gear, the axis of the second bevel gear is vertical to the axis of the second gear, the double-sided side gear is arranged between the first gear and the second gear, one surface of the double-sided side gear is constantly meshed with the first bevel gear, the other surface of the double-sided side gear is constantly meshed with the second bevel gear, the axis of the double-sided side gear is overlapped with the axis of the first gear, the duplicate gear is rotatably arranged in a shell and is constantly meshed with the first gear and the second gear respectively, the second bevel gear is in constant meshing with the driven side gear to output power, a third gear is coaxially and fixedly arranged on the driven side gear, and a fourth gear in constant meshing with the third gear and a fifth gear in coaxial transmission connection with the fourth gear are arranged in the shell;
the transmission ratio of power passing through the first bevel gear, the double-sided side gear and the second bevel gear from the driving side gear is different from the transmission ratio of power passing through the first bevel gear, the first gear, the duplicate gear, the second gear and the second bevel gear in sequence;
the gear shifting mechanism comprises an output shaft, a first output gear and a second output gear, and is characterized by further comprising a gear shifting assembly, wherein the gear shifting assembly comprises an external spline coaxially and fixedly connected to the output shaft, an internal spline sliding sleeve sleeved on the external spline and capable of axially sliding, and the first output gear and the second output gear are positioned on two sides of the external spline;
a transmission shaft is coaxially and fixedly arranged on the second sun gear, a sixth gear and a seventh gear are fixedly arranged on the transmission shaft, the third gear sequentially transmits power to a fifth gear through a fourth gear, the fifth gear is respectively and normally meshed with the first output gear and the sixth gear, the seventh gear is normally meshed with the second output gear, and when the internal spline sliding sleeve is combined with the first output gear, the external spline drives the output shaft to be positively changed into a forward gear; when the internal spline sliding sleeve is combined with the second output gear, the external spline drives the output shaft to reversely rotate to reverse gear.
Compared with the prior art, the invention has the following beneficial effects: the mechanical gear type stepless automatic transmission combines the advantages of an MT transmission and a CVT transmission, has quick acceleration response, can bear large torque, has no pause and frustration, has quick transmission ratio change speed and low manufacturing cost.
Drawings
FIG. 1 is a schematic structural diagram of the present invention.
Detailed Description
The invention will be further described with reference to the accompanying drawings and specific embodiments.
Example 1
Referring to fig. 1, the continuously variable automatic transmission provided by the present invention comprises a housing, an input shaft 1 and an output shaft 2 which are sleeved on the housing, and further comprises a first planetary row which is arranged inside the housing, wherein the input shaft 1 is fixedly connected with a first input gear 7, a first ring gear 3 is sleeved and fixed with a second input gear 8 which is normally engaged with the first input gear 7, the first planetary row comprises a first ring gear 3 which is engaged with the input shaft 2 for transmission, a plurality of (at least two) first planetary gears 4, a first planet carrier 5 and a first sun gear 6, the first planetary gears 4 are rotatably mounted on the first planet carrier 5 and are normally engaged with inner teeth of the first ring gear 3 and outer teeth of the first sun gear 6, respectively, the first sun gear 6 transmits power to the output shaft 2, and further comprises a second planetary row which is arranged inside the housing, and the second planetary row comprises a second ring gear, a plurality of second planetary gears 9, The second planet carrier and the second sun gear 10, but the rotation of second planet wheel 9 is installed on the second planet carrier and with the internal tooth of second ring gear and the external tooth constant mesh of second sun gear 10 respectively, wherein first ring gear 3 and second ring gear are same ring gear (share same ring gear), first planet carrier 5 and second planet carrier are same planet carrier (share same planet carrier, and the diameter of second planet wheel 9 installation department is greater than the diameter of first planet wheel 4 installation department), first sun gear 6 is connected through the gear drive with second sun gear 10.
The first sun gear 6 can rotate automatically, the second sun gear 10 can only rotate in one direction and the rotation direction of the second sun gear is limited to be opposite to or not rotating with the rotation direction of the first gear ring 3 through the first one-way bearing 11, the first planet carrier 5 can only rotate in one direction and the rotation direction of the first planet carrier is limited to be the same as or not rotating with the rotation direction of the first gear ring 3 through the second one-way bearing 12, and the number of teeth of the first sun gear 6 is smaller than that of the second sun gear 10. The first planet row and the second planet row share the gear ring and the planet carrier, when the stepless automatic transmission works and moves, the problem that the running rotating speeds of the planet rows are different is solved, the rotating speeds of the two sets of gear rings are always synchronous, the rotating speeds of the planet carrier are always synchronous, the first sun gear and the second sun gear are connected through gear transmission, the problem that the transmission ratio needs to be changed by an auxiliary system is solved in the operation process, and the effect of automatically adjusting the transmission ratio according to the external resistance is achieved. The problem that the rotating speeds of the second sun gear, the first sun gear and the first planet carrier are uncertain is solved through the one-way bearing, and the purposes that the first sun gear and the second sun gear can be locked to rotate and the planet carrier can be locked to rotate under any condition are achieved.
Example 2
Unlike embodiment 1, the present invention further includes a differential gear train disposed inside the housing, the differential gear train including a driving side gear 13 coaxially connected to the first sun gear 6 in a transmission manner, a driven side gear 14, a first gear 15 and a second gear 16 disposed side by side, a plurality of (at least two) first bevel gears 17 mounted on the first gear 15 and constantly engaged with the driving side gear 13 and rotatable, a plurality of (at least two) second bevel gears 18 mounted on the second gear 16 and rotatable, and a double gear 19, an axis of the first bevel gear 17 being perpendicular to an axis of the first gear 15, an axis of the second bevel gear 18 being perpendicular to an axis of the second gear 16, a double-sided side gear 20 disposed inside the housing between the first gear 15 and the second gear 16, an axis of the double-sided gear 20 being coincident with an axis of the first gear 15, one side of the double-sided gear 20 being constantly engaged with the first bevel gear 17, the other side of the double gear is constantly meshed with a second bevel gear 18, a duplicate gear 19 is rotatably arranged in the shell and constantly meshed with a first gear 15 and a second gear 16 respectively, the second bevel gear 18 is constantly meshed with a driven side gear 14 to output power, a third gear 21 is coaxially and fixedly arranged on the driven side gear 14, and the first sun gear 6 transmits the power to an output shaft through the third gear 21. The transmission ratio of power passing through the first bevel gear 17, the double-sided side gear 20 and the second bevel gear 18 in sequence from the driving side gear 13 is smaller than the transmission ratio of power passing through the first bevel gear 17, the first gear 15, the double gear 19, the second gear 16 and the second bevel gear 18 in sequence. The first sun gear and the second sun gear have different tooth numbers, so that the purpose of matching the maximum rotation speed ratio and the minimum rotation speed ratio of the differential gear train can be achieved.
The third gear is in transmission connection with the second sun gear through a transmission mechanism, specifically, the transmission mechanism in this embodiment includes a fourth gear 22 and a fifth gear 23, a transmission shaft 29 is coaxially and fixedly disposed on the second sun gear 10, a sixth gear 30 is fixedly disposed on the transmission shaft 29, the third gear 21 sequentially transmits power to the fifth gear 23 through the fourth gear 22, and the fifth gear 23 is in constant mesh with the sixth gear 30. The rest of the structure of this embodiment is the same as that of embodiment 1, and is not described herein again.
The problem that the transmission ratio cannot be automatically adjusted due to external resistance change is solved by simultaneously outputting different transmission ratios through two routes, and the effect of stepless automatic adjustment of transmission ratio output between the maximum transmission ratio and the minimum transmission ratio is achieved. First sun gear passes through gear drive by the third gear through differential gear and is connected with the second sun gear, can solve the little limitation of current derailleur drive ratio variation range, solves the problem that current CVT derailleur can not bear big moment of torsion simultaneously, can automatic speed governing and scope increase, can bear big moment of torsion output again.
Example 3
Different from the embodiment 2, the present embodiment further includes a gear shift assembly installed in the housing, the gear shift assembly includes an external spline 24 coaxially and fixedly connected to the output shaft 2, an internal spline sliding sleeve 25 sleeved on the external spline 24, a first output gear 26 and a second output gear 27 located at two sides of the external spline 24, and both the first output gear 26 and the second output gear 27 are provided with sliding shafts 28 matched with the internal spline sliding sleeve 25; the fifth gear 23 is constantly meshed with the first output gear 26, a seventh gear 31 is fixedly arranged on the transmission shaft 29, the seventh gear 31 is constantly meshed with the second output gear 27, and when the internal spline sliding sleeve 25 is combined with the first output gear 26, the external spline 24 drives the output shaft 2 to rotate forward to be a forward gear; when the internal spline sliding sleeve 25 is combined with the second output gear 27, the external spline 24 drives the output shaft 2 to reversely rotate to reverse gear. The rest of the structure of this embodiment is the same as that of embodiment 2, and is not described herein again. The gear shifting assembly is provided with a forward gear and a backward gear, the problem that the existing manual transmission vehicle frequently shifts gears during running is solved, the operation is rapid and convenient, and the forward gear and the backward gear have the function of stepless automatic speed change.
The working principle of the invention is as follows:
according to the law of conservation of energy, the characteristic equation of the motion law of the single-row planetary gear mechanism is as follows:
n1+an2-(1+a)n30, wherein n1The sun gear rotation speed; n is2The gear ring rotation speed; n is3The rotational speed of the planet carrier. In the first planetary row and the second planetary row n2When the number of teeth of the sun gear of the second planet row is larger than that of the sun gear of the first planet row, if the first sun gear and the second sun gear do not rotate and simultaneously drive the gear ring, the rotating speed of the first planet carrier is larger than that of the second planet carrier; if the first planet carrier and the second planet carrier do not rotate and simultaneously drive the gear ring, the rotating speed of the first sun gear is greater than that of the second sun gear. According to the design of the transmission, the first planet row and the second planet row share a gear ring and a planet carrier, the second sun gear 10 can not rotate in the same direction with the gear ring to drive the gear ring, the planet carrier moves according to the track of the second planet row, the first planet row sun gear must rotate reversely to make up the rotation speed difference of the planet carrier (the rotation speed of the first sun gear 6 is always greater than that of the second sun gear 10), if the planet carrier does not rotate, the gear ring is driven, at the moment, the rotation speed ratio of the first sun gear 6 to the second sun gear 10 is minimum, the rotation speed ratio of the gear ring to the output sun gear (the second sun gear) is minimum, accordingly, the rotation speed ratio of the first sun gear 6 to the second sun gear 10 is small, and the rotation speed ratio of the ring gear to the output sun gear (second sun gear) is small, and accordingly, the rotation speed ratio of the first sun gear 6 to the second sun gear 10 is large, and the rotation speed ratio of the ring gear to the output sun gear (second sun gear) is large.
The change of the rotating speed ratio of the first sun gear 6 and the second sun gear 10 corresponds to the change of the rotating speed ratio of the gear ring and the output sun gear, the change range of the rotating speed ratio of the first sun gear is small, the change range of the rotating speed ratio of the second sun gear is large, namely, the first planet row and the second planet row share the combination of the gear ring and the planet carrier, the rotating speed ratio of the first sun gear 6 and the second sun gear 10 in a small interval is input, the rotating speed ratio of the output gear ring and the output sun gear (the second sun gear) in a large interval is corresponding to the rotating speed ratio of the output gear ring and the output sun gear, the maximum transmission ratio of the current automobile speed changer is about 5:1, the transmission ratio of the gear ring and the output sun gear is about 1.2:1, the rotating speed ratio of the first sun gear 6 and the second sun gear 10 is small, the rotating speed ratio of the planet carrier is small, the transmission ratio of the gear ring and the output sun gear is small, the rotating speed ratio of the first sun gear 6 and the second sun gear 10 is minimum (about 1.042:1), the planet carrier does not rotate, the transmission ratio of the gear ring to the output sun gear is minimum, so the rotating speed ratio interval of the first sun gear 6 and the second sun gear 10 is 1.2:1-1.042:1, and the rotating speed ratio change of the first sun gear 6 and the second sun gear 10 is completed by a differential gear train.
The rotational speed of ring gear is in step with the rotational speed of engine, and the rotational speed of planet carrier depends on the rotational speed of second sun gear 10, and second sun gear 10 rotational speed is slow, then the planet carrier rotational speed is fast, otherwise second sun gear 10 rotational speed is fast, then the planet carrier rotational speed is slow, and the rotational speed of first sun gear 6 depends on the rotational speed of planet carrier, and the planet carrier rotational speed is fast, then the rotational speed of first sun gear 6 is slow, and the planet carrier rotational speed is slow, then the rotational speed of first sun gear 6 is fast. A differential gear train automatic speed regulation device is characterized in that power is output to a driving side gear 13 from a first sun gear 6, the driving side gear 13 transmits the power to a second sun gear 10 and an output shaft 2 through two transmission lines with different transmission ratios, the two transmission lines with different transmission ratios respectively correspond to the corresponding transmission ratio and the minimum transmission ratio (1.042:1) of the first sun gear 6 and the second sun gear 10, the transmission ratio of the power passing through a first bevel gear 17, a double-sided side gear 20 and a second bevel gear 18 (line A) from the driving side gear 13 in sequence is smaller than the transmission ratio passing through the first bevel gear 17, the first gear 15, a double-coupled gear 19, the second gear 16 and the second bevel gear 18 (line B) in sequence, namely, the line B is labor-saving transmission, the first gear 15 (a planet carrier) and the second gear 16 (a planet carrier) and the double-coupled gear 19 do not rotate when the line A is passed, the double-sided side gear 20 rotates, the rotation direction is opposite to the rotation direction of the driving side gear 13 and the driven side gear 14, the double-sided side gear 20 does not rotate when the B line is taken, and the first gear 15 and the second gear 16 rotate and are the same as the rotation direction of the driving side gear 13 and the driven side gear 14. According to the principle and formula of the differential, when the vehicle starts, rated rotational speed power is input, power is input to the driving side gear 13, the line A is in direct transmission, the power is transmitted by the line A1: 1, the minimum transmission ratio (1.042:1) of the first sun gear 6 and the second sun gear 10 is corresponded, the transmission ratio of the input ring gear and the output sun gear (second sun gear) is minimum, the line A can not transmit, the power is forced to enter the line B, the line B is involved, under the combined action of the line A and the line B, the torque borne by the second gear 16 is larger than that of the first gear 15, the torque borne by the driven side gear 14 is larger than that of the double-sided side gear 20, and the steering direction of the double-sided side gear 20 is the same as that of the driving side gear 13, the first gear 15, the second gear 16 and the driven side gear 14, and the rotation speed of the duplex gear 19 is consistent with that of the driving side gear 13, the rotation direction of the duplex gear 19 is opposite to that of the first gear 15 and the second gear 16, the transmission ratio of power from the driving side gear 13 to the driven side gear 14 is larger than that of a B line (starting transmission ratio), the transmission ratio reaches the maximum value (1.2:1), and the transmission ratio of an input gear ring to an output sun gear (second sun gear) is the maximum value (5: 1). If the power is sufficient and the vehicle is inertially excited and the maximum (starting gear ratio) driving force is no longer required, the combined force of the a-line and the B-line changes, the rotational speed of the double-sided side gear 20 slows down, or stops rotating, and when the double-sided side gear 20 slows down to stop rotating, the power transmission ratio from the driving side gear 13 to the driven side gear 14 changes to the B-line gear ratio. By this time, the transmission ratio of the power from the driving side gear 13 to the driven side gear 14 becomes small. When the inertia is increased and the speed is increased, the double-sided gear 20 is changed from the stop to the reverse rotation, that is, the rotation direction of the double-sided gear 20 is opposite to the rotation direction of the driving gear 13, the first gear 15, the second gear 16 and the driven gear 14, the transmission ratio of the power from the driving gear 13 to the driven gear 14 is smaller than the transmission ratio of the B-line, when the inertia is increased and the speed is increased, the rotation speed of the double-sided gear 19 is changed from fast to slow, the transmission ratio of the driving gear 13 to the driven gear 14 is further smaller than the transmission ratio of the B-line, the rotation speed ratio of the corresponding first sun gear 6 to the corresponding second sun gear 10 is reduced, the rotation speed of the carrier is reduced, the transmission ratio of the input ring gear to the output sun gear (second sun gear 10) is reduced, the reverse rotation of the double-sided gear 20 is increased, and the transmission ratio is accordingly reduced. The above vehicle acceleration process. When the vehicle accelerates to a certain speed and the input power and the external resistance of the vehicle are balanced, the rotating speeds of the first gear 15, the second gear 16 and the double-sided side gear 20 are not changed, and the vehicle runs at a constant speed. When the vehicle slides with gear, the line A is labor-saving transmission because of the state of reaction force, under the action of inertia force, the second sun gear 10 is transmitted with the first sun gear 6 through the line A in the differential gear train, at the moment, the transmission ratio of the first sun gear 6 and the second sun gear 10 is minimum, the first gear 15, the second gear 16 and the duplicate gear 19 do not rotate, and the planet carrier is locked by the one-way bearing and is in a stop rotation state. When the bicycle is accelerated after sliding, the planet carrier and the gear ring rotate in the same direction, power is transmitted to the second sun gear 10 and the output shaft 2 from the first sun gear 6 through the combined action of an AB line in the differential gear train, and the rotation changes of the first gear 15, the second gear 16 and the double-sided side gear 20 are automatically matched to generate corresponding transmission ratios along with the influence of the speed of the bicycle. When the vehicle runs from starting, accelerating, uniform-speed and sliding to reaccelerating, the transmission ratio change from the driving side gear 13 to the driven side gear 14 automatically matches the change of the rotation speed of the first gear 15 and the second gear 16 and the change of the rotation speed and the rotation speed of the double-sided side gear 20. The differential gear train speed regulating device has the advantages that the transmission change process is continuous and can be automatically matched with the optimal transmission ratio all the time from the starting transmission ratio, namely the transmission ratio of a B line, the transmission ratio of an AB line interval, and the transmission ratio of an A line, and the stepless automatic speed change is realized by gear meshing transmission and planet wheel transmission in the whole process.
In a word, the mechanical gear type stepless automatic transmission has the characteristics of quick acceleration response, smooth gear shifting and capability of bearing large torque output, and has popularization and application values.
The above description is only for the purpose of illustrating the preferred embodiments of the present invention and should not be taken as limiting the invention, so that any modifications, equivalents, improvements and the like, which are within the spirit and principle of the present invention, should be included in the scope of the present invention.
Claims (8)
1. A mechanical gear type stepless automatic speed changer is characterized in that: the planetary gear set comprises a first planetary row arranged in a shell, wherein the first planetary row comprises a first gear ring in meshing transmission with an input shaft, a plurality of first planetary gears, a first planet carrier and a first sun gear, the first planetary gears can be arranged on the first planetary carrier in a self-rotating mode and are respectively and normally meshed with inner teeth of the first gear ring and outer teeth of the first sun gear, the first sun gear transmits power to an output shaft, the planetary gear set also comprises a second planetary row arranged in the shell, the second planetary row comprises a second gear ring, a plurality of second planetary gears, a second planet carrier and a second sun gear, the second planetary gears can be arranged on the second planet carrier in a self-rotating mode and are respectively and normally meshed with inner teeth of the second gear ring and outer teeth of the second sun gear, the first gear ring and the second gear ring are the same gear ring, and the first planet carrier and the second planet carrier are the same planet carrier, the first sun gear is in transmission connection with the second sun gear through a gear;
the first sun gear can rotate automatically, the second sun gear is limited by a one-way bearing to rotate only in one direction, the rotation direction of the second sun gear is opposite to the rotation direction of the gear ring, the first planet carrier is limited by another one-way bearing to rotate only in one direction, the rotation direction of the first planet carrier is the same as or not rotating with the rotation direction of the gear ring, and the number of teeth of the first sun gear is less than that of the second sun gear;
the differential gear train comprises a driving side gear, a driven side gear, a first gear, a second gear, a plurality of first bevel gears, a plurality of second bevel gears and a duplicate gear, wherein the driving side gear is in transmission connection with the first sun gear, the first gear and the second gear are arranged side by side, the first bevel gears are arranged on the first gear, are in constant meshing with the driving side gear and can rotate, the second bevel gears are arranged on the second gear, are in rotation, double-sided side gears are arranged between the first gear and the second gear, one surfaces of the double-sided side gears are in constant meshing with the first bevel gears, the other surfaces of the double-sided side gears are in constant meshing with the second bevel gears, the duplicate gear is rotatably arranged in the shell and is in constant meshing with the first gear and the second gear respectively, the second bevel gears are in constant meshing with the driven side gear, and a third gear is coaxially and fixedly arranged on the driven side gear, the first sun gear is transmitted to the second sun gear and the output through a third gear and a gear.
2. The mechanical gear type continuously variable automatic transmission according to claim 1, characterized in that: the transmission ratio of power passing through the first bevel gear, the double-sided side gear and the second bevel gear from the driving side gear is different from the transmission ratio of power passing through the first bevel gear, the first gear, the duplicate gear, the second gear and the second bevel gear in sequence.
3. The mechanical gear type continuously variable automatic transmission according to claim 2, characterized in that: the third gear is in transmission connection with the second sun gear through a transmission mechanism, the transmission mechanism comprises a fourth gear in constant mesh with the third gear and a fifth gear in coaxial transmission connection with the fourth gear, a transmission shaft is coaxially and fixedly arranged on the second sun gear, a sixth gear is fixedly arranged on the transmission shaft, the third gear transmits power to the fifth gear sequentially through the fourth gear, and the fifth gear is in constant mesh with the sixth gear.
4. The mechanical gear type continuously variable automatic transmission according to claim 3, characterized in that: the gear shifting assembly comprises an external spline, an internal spline sliding sleeve, a first output gear and a second output gear, wherein the external spline is coaxially and fixedly connected to the output shaft; the fifth gear is in constant mesh with the first output gear, a seventh gear is fixedly arranged on the transmission shaft and is in constant mesh with the second output gear, and when the internal spline sliding sleeve is combined with the first output gear, the external spline drives the output shaft to be positively changed into a forward gear; when the internal spline sliding sleeve is combined with the second output gear, the external spline drives the output shaft to reversely rotate to reverse gear.
5. The mechanically-geared continuously automatic transmission according to claim 4, characterized in that: the axis of the first bevel gear is vertical to the axis of the first gear, and the axis of the second bevel gear is vertical to the axis of the second gear.
6. The mechanical gear type continuously variable automatic transmission according to claim 5, characterized in that: the driving side gear is in coaxial transmission connection with the first sun gear.
7. The mechanically-geared continuously automatic transmission according to claim 6, characterized in that: the input shaft and the output shaft are sleeved on the shell.
8. The mechanical gear type continuously variable automatic transmission according to any one of claims 1 to 7, characterized in that: the input shaft is fixedly connected with a first input gear, and a second input gear which is constantly meshed with the first input gear is fixedly sleeved outside the first gear ring.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710671797.1A CN107269782A (en) | 2017-08-08 | 2017-08-08 | Mechanical gear formula ST |
| CN2017106717971 | 2017-08-08 |
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| CN108386496A CN108386496A (en) | 2018-08-10 |
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| CN201810426023.7A Active CN108386496B (en) | 2017-08-08 | 2018-05-07 | Mechanical gear type stepless automatic speed variator |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN107781364B (en) * | 2017-11-28 | 2024-03-01 | 重庆帝勒金驰通用机械股份有限公司 | Power transmission mechanism of gearbox of mini-tiller |
| CN112032276B (en) * | 2019-06-03 | 2021-07-20 | 哈尔滨工业大学 | Six-shaft differential device based on gear transmission |
| CN112032275B (en) * | 2019-06-03 | 2021-07-20 | 哈尔滨工业大学 | Mechanical four-axis differential device |
| CN113212158A (en) * | 2021-06-07 | 2021-08-06 | 银川威力传动技术股份有限公司 | Coaxial planetary power transmission axle and new energy automobile using same |
Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2517617Y (en) * | 2002-01-24 | 2002-10-23 | 新疆升晟股份有限公司 | Four-wheel differental torque divider |
| CN1865732A (en) * | 2006-05-13 | 2006-11-22 | 吴秋明 | Mechanical stepless automatic transmission |
| CN1959147A (en) * | 2006-07-05 | 2007-05-09 | 徐强国 | Steep less gear of planet gear |
| CN2902896Y (en) * | 2006-03-28 | 2007-05-23 | 孟国华 | Reversion speed changer of bilayer screw propeller helicopter |
| CN101446330A (en) * | 2007-11-26 | 2009-06-03 | 徐强国 | Two-freedom satellite gear stepless transmission |
| GB2466968A (en) * | 2009-01-16 | 2010-07-21 | Gm Global Tech Operations Inc | Hybrid vehicle with auxiliary drive member providing an offset torque |
| CN106286726A (en) * | 2015-06-11 | 2017-01-04 | 王亚 | A kind of planetary gear type auxiliary transmission |
| CN107664194A (en) * | 2016-07-28 | 2018-02-06 | 钟跃荣 | A kind of mechanical stepless speed change method and buncher |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP4513492B2 (en) * | 2004-10-13 | 2010-07-28 | 株式会社ジェイテクト | Differential device and vehicle driving force transmission unit using the same |
-
2017
- 2017-08-08 CN CN201710671797.1A patent/CN107269782A/en active Pending
-
2018
- 2018-05-07 CN CN201810426023.7A patent/CN108386496B/en active Active
Patent Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2517617Y (en) * | 2002-01-24 | 2002-10-23 | 新疆升晟股份有限公司 | Four-wheel differental torque divider |
| CN2902896Y (en) * | 2006-03-28 | 2007-05-23 | 孟国华 | Reversion speed changer of bilayer screw propeller helicopter |
| CN1865732A (en) * | 2006-05-13 | 2006-11-22 | 吴秋明 | Mechanical stepless automatic transmission |
| CN1959147A (en) * | 2006-07-05 | 2007-05-09 | 徐强国 | Steep less gear of planet gear |
| CN101446330A (en) * | 2007-11-26 | 2009-06-03 | 徐强国 | Two-freedom satellite gear stepless transmission |
| GB2466968A (en) * | 2009-01-16 | 2010-07-21 | Gm Global Tech Operations Inc | Hybrid vehicle with auxiliary drive member providing an offset torque |
| CN106286726A (en) * | 2015-06-11 | 2017-01-04 | 王亚 | A kind of planetary gear type auxiliary transmission |
| CN107664194A (en) * | 2016-07-28 | 2018-02-06 | 钟跃荣 | A kind of mechanical stepless speed change method and buncher |
Also Published As
| Publication number | Publication date |
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| CN108386496A (en) | 2018-08-10 |
| CN107269782A (en) | 2017-10-20 |
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