CN109681592B - Seven-front-two-reverse planetary transmission - Google Patents

Seven-front-two-reverse planetary transmission Download PDF

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Publication number
CN109681592B
CN109681592B CN201811444514.0A CN201811444514A CN109681592B CN 109681592 B CN109681592 B CN 109681592B CN 201811444514 A CN201811444514 A CN 201811444514A CN 109681592 B CN109681592 B CN 109681592B
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China
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gear
clutch
planet
fixedly connected
ring
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CN109681592A (en
Inventor
何融
程燕
张玉东
张强
许晋
李洪武
李亮
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China North Vehicle Research Institute
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China North Vehicle Research Institute
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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
    • F16H3/62—Gearings having three or more central gears
    • 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
    • F16H59/00—Control inputs to control units of change-speed-, or reversing-gearings for conveying rotary motion
    • F16H59/02—Selector apparatus
    • 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
    • F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
    • F16H2200/0056—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising seven forward speeds
    • 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
    • F16H2200/0082—Transmissions for multiple ratios characterised by the number of reverse speeds
    • F16H2200/0086—Transmissions for multiple ratios characterised by the number of reverse speeds the gear ratios comprising two reverse speeds
    • 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
    • F16H2200/2012—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with four sets of orbital gears
    • 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
    • F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
    • F16H2200/2043—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with five engaging means

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Structure Of Transmissions (AREA)

Abstract

The invention discloses a seven-front-two reverse planetary transmission, which belongs to the technical field of transmissions and comprises: the planetary gear train comprises an input shaft, an output shaft, a planetary gear train, a clutch and a brake; the four planet rows are distributed in parallel; the input shaft is coaxially and fixedly connected with the second sun gear; the first planet carrier is fixedly connected with the second gear ring; the first gear ring is fixedly connected with the third sun gear; the second planet carrier is fixedly connected with the fourth gear ring; the third gear ring is fixedly connected with the fourth planet carrier; the fourth planet carrier is fixedly connected with the output shaft; an outer hub of the first clutch is fixedly connected with the third planet carrier, and an inner hub of the first clutch is fixedly connected with the first planet carrier; an inner hub of the second clutch is fixedly connected with the first sun gear, and an outer hub of the second clutch is fixedly connected with the input shaft; an outer hub of the third clutch is fixedly connected with the first gear ring, and an inner hub of the third clutch is fixedly connected with the second planet carrier; the inner hub of the first brake is fixedly connected with the fourth sun gear; an inner hub of the second brake is fixedly connected with the third planet carrier; the outer hubs of the first brake and the second brake are fixed on the transmission shell; the invention can reduce the number of the operating pieces and improve the efficiency.

Description

Seven-front-two-reverse planetary transmission
Technical Field
The invention belongs to the technical field of transmissions, and particularly relates to a seven-front-two reverse planetary transmission.
Background
The speed change mechanism of the automatic gearbox changes the rotating speed and the torque output by the hydraulic torque converter, and outputs the changed rotating speed and the changed torque through the output shaft so as to meet the actual requirement. The more gears of the automatic gearbox are, the smoother the gear shifting is, the better the power performance and the fuel economy are, and therefore the scheme of realizing more gears is used as far as possible.
The existing commercial vehicles mainly use three-degree-of-freedom planetary transmissions, at least five operating elements are needed for realizing multiple gears, the existing transmissions have six operating elements and even seven operating elements, and the power loss of the planetary transmissions is mostly generated by the operating elements.
The realization of the gear of the multi-degree-of-freedom planetary transmission is realized by combining different control pieces, excessive control pieces occupy excessive space, and when the control pieces are not combined, belt row loss exists, so that the more the control pieces are, the better the control pieces are. When the planetary transmission uses five operating elements, two operating elements are required to be jointed when the three degrees of freedom work, and the remaining three elements are opened, so that power loss is generated. When the four-degree-of-freedom work is carried out, three control elements are combined, and the rest two elements are opened, so that the power loss is effectively reduced. Moreover, the operating parts are coupled differently between different gears, which requires fewer operating parts to be switched during a gear change, which makes the gear change easier and more reliable.
Disclosure of Invention
In view of this, the invention provides a seven-front-two reverse planetary transmission, which can reduce the number of operating pieces and improve the efficiency while ensuring multiple gears.
The invention is realized by the following technical scheme:
a seven-first two-reverse planetary transmission comprising: the planetary gear train comprises an input shaft, an output shaft, four planetary rows, three clutches and two brakes;
each planet row comprises: the planetary gear set comprises a gear ring, a planetary carrier, a sun gear and a planetary gear; the gear ring and the sun gear are coaxially distributed, more than three planet gears are respectively arranged on the planet carrier through bearings and planet gear shafts, and each planet gear is simultaneously meshed with the gear ring and the sun gear;
the four planet rows are distributed in parallel, the four sun wheels are coaxial, and the four planet rows are a first planet row, a second planet row, a third planet row and a fourth planet row from left to right in sequence; the first planet row comprises the following components: the planetary gear set comprises a first gear ring, a first planet carrier, a first sun gear and a first planet gear; the second planet row comprises the following components: the second gear ring, the second planet carrier, the second sun gear and the second planet gear; the third planetary row comprises the following components: a third gear ring, a third planet carrier, a third sun gear and a third planet gear; the component parts of the fourth planet row are as follows: the fourth gear ring, the fourth planet carrier, the fourth sun gear and the fourth planet gear;
the input shaft is coaxially and fixedly connected with the second sun gear; the first planet carrier is fixedly connected with the second gear ring; the first gear ring is fixedly connected with the third sun gear; the second planet carrier is fixedly connected with the fourth gear ring; the third gear ring is fixedly connected with the fourth planet carrier; the fourth planet carrier is fixedly connected with the output shaft, and the input shaft is coaxial with the output shaft;
the three clutches are respectively a first clutch, a second clutch and a third clutch; an outer hub of the first clutch is fixedly connected with the third planet carrier, and an inner hub of the first clutch is fixedly connected with the first planet carrier; an inner hub of the second clutch is fixedly connected with the first sun gear, and an outer hub of the second clutch is fixedly connected with the input shaft; an outer hub of the third clutch is fixedly connected with the first gear ring, and an inner hub of the third clutch is fixedly connected with the second planet carrier;
the two brakes are respectively a first brake and a second brake; the inner hub of the first brake is fixedly connected with the fourth sun gear; an inner hub of the second brake is fixedly connected with the third planet carrier; the outer hub of the first brake and the outer hub of the second brake are both fixed to the transmission housing.
Further, initially, the three clutches and the two brakes are in an unengaged state;
combining the first clutch, the second clutch and the second brake to form a first forward gear;
combining the second clutch, the first brake and the second brake to form a second forward gear;
combining the first clutch, the first brake and the second brake to form a third forward gear;
combining the first clutch, the second clutch and the first brake to form a fourth forward gear;
combining the first clutch, the third clutch and the first brake to form a fifth forward gear;
combining the second clutch, the third clutch and the first brake to form a sixth forward gear;
combining the first clutch, the second clutch and the third clutch to form a seventh forward gear;
combining the first clutch, the third clutch and the second brake to form a first reverse gear;
and combining the second clutch, the third clutch and the second brake to form a second reverse gear.
Further, k values of the four planet rows are respectively, wherein the k value is the gear ratio of the ring gear to the sun gear of each planet row:
the gear ratio of the first ring gear to the first sun gear is: zR1/ZS1＝3.182；
The gear ratio of the second gear ring to the second sun gear is as follows: zR2/ZS2＝1.8；
The gear ratio of the third ring gear to the third sun gear is: zR3/ZS3＝2.198；
The gear ratio of the fourth ring gear to the fourth sun gear is: zR4/ZS4＝3。
Has the advantages that: (1) the invention is provided with four planet rows, three clutches and two brakes, namely seven forward gears and two reverse gears of the transmission can be realized by only using five control parts, the transmission ratio range is large, the highest transmission ratio can reach 6.994, and the performance is excellent; and each gear is realized by only combining three operating pieces, thereby effectively reducing the power loss of the belt row, reducing the size of the automatic gearbox by using fewer operating pieces, lightening the weight of the gearbox and reducing the manufacturing cost.
(2) The four planet rows are all internally and externally meshed single-planet rows, the k value is within the range of 1.6-3.5, the radial size of the four planet rows is reduced, and the transmission ratio characteristic with better overall performance can be obtained.
(3) The adjacent gears of seven forward gears and two reverse gears are switched by only one operating piece, so that the gear shifting control is simple and easy, and the reliability is high.
Drawings
FIG. 1 is a structural component diagram of the present invention;
Detailed Description
The invention is described in detail below by way of example with reference to the accompanying drawings.
The present embodiment provides a seven-first two-reverse planetary transmission, including: referring to fig. 1 (wherein the invention is an axisymmetric structure, fig. 1 is a schematic half view of the axisymmetric structure), including: the planetary gear train comprises an input shaft, an output shaft, four planetary rows, three clutches and two brakes;
each planet row comprises: the planetary gear set comprises a gear ring, a planetary carrier, a sun gear and a planetary gear; the gear ring and the sun gear are coaxially distributed, more than three planet gears are respectively arranged on the planet carrier through bearings and planet gear shafts, and each planet gear is simultaneously meshed with the gear ring and the sun gear;
the four planet rows are distributed in parallel, the four sun wheels are coaxial, and the four planet rows are a first planet row, a second planet row, a third planet row and a fourth planet row from left to right in sequence; the first planet row comprises the following components: a first ring gear R1, a first carrier PC1, a first sun gear S1, and a first planet gear P1; the second planet row comprises the following components: a second ring gear R2, a second planet carrier PC2, a second sun gear S2, and second planet gears P2; the third planetary row comprises the following components: a third ring gear R3, a third carrier PC3, a third sun gear S3, and a third planet gear P3; the component parts of the fourth planet row are as follows: a fourth ring gear R4, a fourth planet carrier PC4, a fourth sun gear S4, and a fourth planet gear P4;
the input shaft is coaxially and fixedly connected with a second sun gear S2; the first planet carrier PC1 is fixedly connected with the second ring gear R2; the first ring gear R1 is fixedly connected with the third sun gear S3; the second planet carrier PC2 is fixedly connected with the fourth ring gear R4; the third gear ring R3 is fixedly connected with a fourth planet carrier PC 4; the fourth planet carrier PC4 is fixedly connected with the output shaft, and the input shaft is coaxial with the output shaft;
the three clutches are a first clutch C1, a second clutch C2 and a third clutch C3 respectively; the outer hub of the first clutch C1 is fixedly connected with the third planet carrier PC3, and the inner hub is fixedly connected with the first planet carrier PC 1; an inner hub of the second clutch C2 is fixedly connected with the first sun gear S1, and an outer hub is fixedly connected with the input shaft; an outer hub of the third clutch C3 is fixedly connected with the first gear ring R1, and an inner hub is fixedly connected with the second planet carrier PC 2;
the two brakes are a first brake B1 and a second brake B2 respectively; the inner hub of the first brake B1 is fixedly connected with the fourth sun gear R4; the inner hub of the second brake B2 is fixedly connected with the third planet carrier PC 3; the outer hub of the first brake B1 and the outer hub of the second brake B2 are fixed to the transmission case.
Thus, the above-described connection relationship constitutes eight rotating members, the first rotating member being: the input shaft, the second sun gear S2 and the second clutch C2 outer hub are fixedly connected; the second rotating member is: the output shaft, the fourth planet carrier PC4 and the third gear ring R3 are fixedly connected; the third rotating member is: the first ring gear R1, the third sun gear S3 and the third clutch C3 are fixedly connected with the outer hub; the fourth rotating member is: the first planet carrier PC1, the second ring gear R2 and the first clutch C1 inner hub are fixedly connected; the fifth rotating member is: the first sun gear S1 and the inner hub of the second clutch C2 are fixedly connected; the sixth rotating member is: the second planet carrier PC2, the third clutch C3 inner hub and the fourth ring gear R4 are fixedly connected; the seventh rotating member is: the third planet carrier PC3, the first clutch C1 outer hub and the second brake B2 inner hub are fixedly connected; the eighth rotating member is: the fourth sun gear S4 and the first brake B1 are fixedly connected; the first brake B1 is for braking the eighth rotating member; the second brake B2 is used for braking the seventh rotating member; the first clutch C1 is used to connect or disconnect the fourth rotating member and the seventh rotating member; the second clutch C2 is used to connect or disconnect the first and fifth rotating members; the third clutch C3 is used to connect or disconnect the third rotating member and the sixth rotating member;
the connection relation forms a four-degree-of-freedom transmission, and five control parts are respectively provided with three clutches and two brakes; three control pieces are combined to realize a certain gear, three degrees of freedom are eliminated, one degree of freedom is left, and fixed input and output can be realized, so that seven forward gears and two reverse gears of the four-degree-of-freedom planetary transmission can be realized by operating five control pieces, and the realization mode is as follows:
initially, the five control pieces are all in an uncombined state;
first forward gear D1: engaging the first clutch C1, the second clutch C2 and the second brake B2; at this time, the third carrier PC3, the first carrier PC1, and the second ring gear R2 are braked;
power is input through an input shaft to drive the first sun gear S1 and the second sun gear S2 to rotate, and when the first sun gear S1 rotates, the first gear ring R1 rotates around the axis of the first sun gear S1 due to braking of the first planet carrier PC 1; the second sun gear S2 rotates, and the second ring gear R2 is braked, so that the second planet carrier PC2 is driven to rotate, the second planet carrier PC2 drives the fourth ring gear R4 to rotate, but because the fourth sun gear S4 is not braked, the fourth ring gear R4 cannot drive the fourth planet carrier PC4 to rotate and output; the second planet row and the fourth planet row do not transmit power;
the first gear ring R1 drives the third sun gear S3 to rotate, and due to braking of the third planet carrier PC3, the third sun gear S3 drives the third gear ring R3 to rotate, so that the fourth planet carrier PC4, namely an output shaft, is driven to rotate to output power;
second forward gear D2: engaging the second clutch C2, the first brake B1 and the second brake B2; at this time, the fourth sun gear S4 and the third planet carrier PC3 brake;
power is input through an input shaft to drive a first sun gear S1 and a second sun gear S2 to rotate, a first planet row and a second planet row work, power is output from a first gear ring R1 and a second planet carrier PC2, the first gear ring R1 drives a third sun gear S3 to rotate (brake of a third planet carrier PC 3), the third sun gear S3 drives a third gear ring R3 to rotate, and the third gear ring R3 drives a fourth planet carrier PC4 to rotate; meanwhile, the second planet carrier PC2 drives the fourth ring gear R4 to rotate, and the fourth ring gear R4 also drives the fourth planet carrier PC4 to rotate because the fourth sun gear S4 is braked;
therefore, the fourth planet carrier PC4 rotates under the combined action of the third ring gear R3 and the fourth ring gear R4, that is, the output shaft rotates for power output;
third forward gear D3: engaging the first clutch C1, the first brake B1 and the second brake B2; at this time, the fourth sun gear S4, the third carrier PC3, the first carrier PC1, and the second ring gear R2 are braked;
power is input through the input shaft, and since the second clutch C2 is not engaged, the first planetary row does not have power input, and therefore the first planetary row does not operate, and further the third planetary row does not have power input, and therefore the third planetary row does not operate;
power is input through the input shaft, the second sun gear S2 is driven to rotate (the second gear ring R2 is braked), the second planet carrier PC2 is driven to rotate, the second planet carrier PC2 drives the fourth gear ring R4 to rotate, and the fourth sun gear S4 is braked, so that the fourth gear ring R4 drives the fourth planet carrier PC4 to rotate, namely, the output shaft rotates to output power;
fourth forward gear D4: engaging the first clutch C1, the second clutch C2, and the first brake B1; at this time, the fourth sun gear S4 is braked;
power is input through an input shaft, the first sun gear S1 and the second sun gear S2 are driven to rotate, the first planet row and the second planet row work, and the power is output from the first gear ring R1 and the second planet carrier PC 2; the first gear ring R1 drives the third sun gear S3 to rotate; the first planet carrier PC1 drives the second gear ring R2 and the third planet carrier PC3 to rotate, and the third gear ring R3 rotates under the action of the third sun gear S3 and the third planet carrier PC3 so as to drive the fourth planet carrier PC4 to rotate; meanwhile, the second planet carrier PC2 drives the fourth ring gear R4 to rotate, and the fourth ring gear R4 drives the fourth planet carrier PC4 to rotate because the fourth sun gear S4 is braked;
therefore, the fourth planet carrier PC4 rotates under the combined action of the third ring gear R3 and the fourth ring gear R4, that is, the output shaft rotates for power output;
fifth forward gear D5: engaging the first clutch C1, the third clutch C3 and the first brake B1; at this time, the fourth sun gear S4 is braked;
power is input through the input shaft, and since the second clutch C2 is not engaged, the first planetary gear does not have power input, so the first planetary gear does not work;
power is input through an input shaft, the second sun gear S2 is driven to rotate, the second planet carrier PC2 and the second gear ring R2 are driven to rotate, and the second gear ring R2 drives the third planet carrier PC3 to rotate through the combined first clutch C1; the second planet carrier PC2 drives the third sun gear S3 to rotate through the combined third clutch; the third gear ring R3 rotates under the action of the third planet carrier PC3 and the third sun gear S3, and the third gear ring R3 drives the fourth planet carrier PC4 to rotate; meanwhile, the second planet carrier PC2 drives the fourth ring gear R4 to rotate, and the fourth ring gear R4 drives the fourth planet carrier PC4 to rotate because the fourth sun gear S4 is braked;
therefore, the fourth planet carrier PC4 rotates under the combined action of the third ring gear R3 and the fourth ring gear R4, that is, the output shaft rotates for power output;
sixth forward gear D6: engaging the second clutch C2, the third clutch C3 and the first brake B1; at this time, the fourth sun gear S4 is braked;
power is input through an input shaft, the first sun gear S1 and the second sun gear S2 are driven to rotate, the first planet row and the second planet row work, and the power is output from the first gear ring R1 and the second planet carrier PC 2; the first gear ring R1 drives the fourth gear ring R4 to rotate together with the second planet carrier PC2 through the combined third clutch C3, and the fourth gear ring R4 drives the fourth planet carrier PC4 to rotate because the fourth sun gear S4 is braked;
meanwhile, although the first ring gear R1 rotates the third sun gear S3, since the third planet carrier PC3 is unconstrained, the third planet carrier does not operate;
therefore, the fourth planet carrier PC4 rotates under the action of the fourth ring gear R4, that is, the output shaft rotates for power output;
seventh forward gear D7: engaging the first clutch C1, the second clutch C2, and the third clutch C3;
power is input through the input shaft, and since the first carrier PC1 is connected to the second ring gear R2, the first ring gear R1 is connected to the second carrier PC2 through the third clutch C3 coupled thereto, the first sun gear S1 is connected to the second sun gear S2 through the second clutch C2 coupled thereto, the third sun gear S3 is connected to the first ring gear R1, and the third carrier PC3 is connected to the first carrier PC1 through the first clutch C1 coupled thereto, the first planetary row, the second planetary row, and the third planetary row rotate integrally; and power is output by the third ring gear R3;
the first gear ring R1 drives the fourth gear ring R4 to rotate through the engaged third clutch C3, but since the fourth sun gear S4 is not braked, the fourth gear ring R4 cannot drive the fourth planet carrier PC4 to rotate, that is, the fourth planet row does not work;
the third gear ring R3 directly drives the fourth planet carrier PC4 to rotate, namely the output shaft rotates to output, and the rotating speed of the output shaft is the same as that of the input shaft as the rotating speed of the third gear ring R3 is the same as that of the input shaft;
first reverse gear R1: engaging the first clutch C1, the third clutch C3 and the second brake B2; the third planet carrier PC3, the first planet carrier PC1 and the second gear ring R2 are braked;
power is input through the input shaft, and since the second clutch C2 is not engaged, the first planetary gear does not have power input, so the first planetary gear does not work;
power is input through an input shaft to drive the second sun gear S2 to rotate, the second ring gear R2 is braked, so that the second sun gear S2 drives the second planet carrier PC2 to rotate, the second planet carrier PC2 drives the third sun gear S3 to rotate through the combined third clutch C3, and the third planet carrier PC3 is braked, so that the third sun gear S3 drives the third ring gear R3 to rotate, and the third ring gear R3 directly drives the fourth planet carrier PC4 to rotate;
meanwhile, the second planet carrier PC2 drives the fourth ring gear R4 to rotate, but because the fourth sun gear S4 is not braked, the fourth ring gear R4 cannot drive the fourth planet carrier PC4 to rotate, that is, the fourth planet row does not work;
therefore, the fourth planet carrier PC4 rotates only by the third ring gear R3, that is, the output shaft rotates for power output;
second reverse gear R2: engaging the second clutch C2, the third clutch C3 and the second brake B2; the third planet carrier PC3 brakes;
power is input through the input shaft, and the first planetary row and the second planetary row rotate integrally because the first planet carrier PC1 is connected with the second ring gear R2, the first ring gear R1 is connected with the second planet carrier PC2 through the combined third clutch C3, and the first sun gear S1 is connected with the second sun gear S2 through the combined second clutch C2; and power is output from the first ring gear R1 and the second planet carrier PC2, since the first ring gear R1 and the second planet carrier PC2 are connected, power can be regarded as being output only from the first ring gear R1;
the first gear ring R1 drives the fourth gear ring R4 to rotate through the engaged third clutch C3, but since the fourth sun gear S4 is not braked, the fourth gear ring R4 cannot drive the fourth planet carrier PC4 to rotate, that is, the fourth planet row does not work;
meanwhile, the first gear ring R1 drives the third sun gear S3 to rotate, and the third planet carrier PC3 brakes, so that the third sun gear S3 drives the third gear ring R3 to rotate, and the third gear ring R3 directly drives the fourth planet carrier PC4 to rotate;
therefore, the fourth planet carrier PC4 rotates only by the third ring gear R3, i.e., the output shaft rotates for power output.
The transmission ratio of each gear of the seven forward gears and the two reverse gears is determined by k values of four planetary rows, and the k value is the gear ratio of a gear ring and a sun gear of each planetary row; in this embodiment, k values of four planetary rows are:
the gear ratio of the first ring gear R1 to the first sun gear S1: zR1/ZS1＝3.182；
The gear ratio of the second ring gear R2 to the second sun gear S2: zR2/ZS2＝1.8；
The gear ratio of the third ring gear R3 to the third sun gear S3: zR3/ZS3＝2.198；
The gear ratio of the fourth ring gear R4 to the fourth sun gear S4: zR4/ZS4＝3。
Thus, the gear ratio of the first forward gear D1 is 6.994, the gear ratio of the second forward gear D2 is 4.714, the gear ratio of the third forward gear D3 is 3.733, the gear ratio of the fourth forward gear D4 is 2.334, the gear ratio of the fifth forward gear D5 is 1.746, the gear ratio of the sixth forward gear D6 is 1.333, the gear ratio of the seventh forward gear D7 is 1.0, the gear ratio of the first reverse gear R1 is-6.154, and the gear ratio of the second reverse gear R2 is-2.198.
In summary, the above description is only a preferred embodiment of the present invention, and is not intended to limit the scope of the present invention. Any modification, equivalent replacement, or improvement made within the spirit and principle of the present invention should be included in the protection scope of the present invention.

Claims (3)

1. A seven-front two-reverse planetary transmission, comprising: the planetary gear train comprises an input shaft, an output shaft, four planetary rows, three clutches and two brakes;
each planet row comprises: the planetary gear set comprises a gear ring, a planetary carrier, a sun gear and a planetary gear; the gear ring and the sun gear are coaxially distributed, more than three planet gears are respectively arranged on the planet carrier through bearings and planet gear shafts, and each planet gear is simultaneously meshed with the gear ring and the sun gear;
the four planet rows are distributed in parallel, the four sun wheels are coaxial, and the four planet rows are a first planet row, a second planet row, a third planet row and a fourth planet row from left to right in sequence; the first planet row includes: the planetary gear set comprises a first gear ring, a first planet carrier, a first sun gear and a first planet gear; the second planetary row includes: the second gear ring, the second planet carrier, the second sun gear and the second planet gear; the third planet row includes: a third gear ring, a third planet carrier, a third sun gear and a third planet gear; the fourth planet row includes: the fourth gear ring, the fourth planet carrier, the fourth sun gear and the fourth planet gear;
the input shaft is coaxially and fixedly connected with the second sun gear; the first planet carrier is fixedly connected with the second gear ring; the first gear ring is fixedly connected with the third sun gear; the second planet carrier is fixedly connected with the fourth gear ring; the third gear ring is fixedly connected with the fourth planet carrier; the fourth planet carrier is fixedly connected with the output shaft, and the input shaft is coaxial with the output shaft;
the three clutches are respectively a first clutch, a second clutch and a third clutch; an outer hub of the first clutch is fixedly connected with the third planet carrier, and an inner hub of the first clutch is fixedly connected with the first planet carrier; an inner hub of the second clutch is fixedly connected with the first sun gear, and an outer hub of the second clutch is fixedly connected with the input shaft; an outer hub of the third clutch is fixedly connected with the first gear ring, and an inner hub of the third clutch is fixedly connected with the second planet carrier;
the two brakes are respectively a first brake and a second brake; the inner hub of the first brake is fixedly connected with the fourth sun gear; an inner hub of the second brake is fixedly connected with the third planet carrier; the outer hub of the first brake and the outer hub of the second brake are both fixed to the transmission housing.
2. A seven-first-two reverse planetary transmission as in claim 1 wherein initially, the three clutches and the two brakes are in an unengaged state;
combining the first clutch, the second clutch and the second brake to form a first forward gear;
combining the second clutch, the first brake and the second brake to form a second forward gear;
combining the first clutch, the first brake and the second brake to form a third forward gear;
combining the first clutch, the second clutch and the first brake to form a fourth forward gear;
combining the first clutch, the third clutch and the first brake to form a fifth forward gear;
combining the second clutch, the third clutch and the first brake to form a sixth forward gear;
combining the first clutch, the second clutch and the third clutch to form a seventh forward gear;
combining the first clutch, the third clutch and the second brake to form a first reverse gear;
and combining the second clutch, the third clutch and the second brake to form a second reverse gear.
3. A seven-first-two reverse planetary transmission as in claim 1 wherein the k values for the four rows are each, wherein k is the ratio of the ring gear to the sun gear of each row:
the gear ratio of the first ring gear to the first sun gear is: zR1/ZS1＝3.182；
The gear ratio of the second gear ring to the second sun gear is as follows: zR2/ZS2＝1.8；
The gear ratio of the third ring gear to the third sun gear is: zR3/ZS3＝2.198；
The gear ratio of the fourth ring gear to the fourth sun gear is: zR4/ZS4＝3。
CN201811444514.0A 2018-11-29 2018-11-29 Seven-front-two-reverse planetary transmission Active CN109681592B (en)

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KR100717304B1 (en) * 2005-12-06 2007-05-15 현대자동차주식회사 7 - shift power train in an automatic transmission for vehicles
KR100897261B1 (en) * 2006-11-06 2009-05-14 현대자동차주식회사 Eight speed powertrain of automatic transmission for vehicle
DE102010042669A1 (en) * 2010-10-20 2012-04-26 Zf Friedrichshafen Ag Multi-speed transmission
DE102010042666A1 (en) * 2010-10-20 2012-04-26 Zf Friedrichshafen Ag Multi-speed transmission
DE102012206808B4 (en) * 2012-04-25 2021-03-11 Zf Friedrichshafen Ag Multi-speed transmission
DE102012206778B4 (en) * 2012-04-25 2021-03-11 Zf Friedrichshafen Ag Multi-speed transmission
CN105299156B (en) * 2015-11-10 2019-02-15 中国北方车辆研究所 A kind of multi-speed transmission
CN106838153B (en) * 2016-12-01 2019-01-08 中国北方车辆研究所 A kind of seven previous planetary transmissions of falling four-degree-of-freedom

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