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CN113074223A - Four-freedom-degree multi-gear planetary speed change mechanism for tracked vehicle - Google Patents

Four-freedom-degree multi-gear planetary speed change mechanism for tracked vehicle Download PDF

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Publication number
CN113074223A
CN113074223A CN202110306538.5A CN202110306538A CN113074223A CN 113074223 A CN113074223 A CN 113074223A CN 202110306538 A CN202110306538 A CN 202110306538A CN 113074223 A CN113074223 A CN 113074223A
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CN
China
Prior art keywords
row
gear
planet
clutch
brake
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
CN202110306538.5A
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Chinese (zh)
Inventor
李慎龙
李新毅
周如意
邢庆坤
唐沛
张静
贾爽
张鹤
尹华兵
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China North Vehicle Research Institute
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China North Vehicle Research Institute
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Publication date
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Priority to CN202110306538.5A priority Critical patent/CN113074223A/en
Publication of CN113074223A publication Critical patent/CN113074223A/en
Pending legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • 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
    • F16H3/66—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another
    • 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
    • F16H57/08—General details of gearing of gearings with members having orbital motion
    • F16H57/10—Braking arrangements
    • 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
    • F16H2200/0091—Transmissions for multiple ratios characterised by the number of reverse speeds the gear ratios comprising three 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
    • F16H2200/2046—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with six 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 belongs to the field of mechanical design, and particularly relates to a four-degree-of-freedom multi-gear planetary speed change mechanism for a tracked vehicle, which has a compact structure, a small size and a plurality of gears. The invention has the advantages of simple planet row connection, simple structure, seven, three and ten gears which can be switched according to the driving working condition, reasonable step ratio selection and convenient automatic gear shifting of the transmission. Compared with the similar speed change mechanism, the planetary speed change mechanism has excellent performance and wide application prospect.

Description

Four-freedom-degree multi-gear planetary speed change mechanism for tracked vehicle
Technical Field
The invention belongs to the field of mechanical design, relates to a design scheme of a speed change mechanism, and particularly relates to a four-degree-of-freedom multi-gear planetary speed change mechanism for a tracked vehicle.
Background
The speed change mechanism of the automatic gearbox outputs the changed rotating speed and torque through the output shaft by changing the rotating speed and torque output by the engine so as to meet the running requirement of the vehicle. Compared with fixed-shaft transmission, the planetary transmission has the advantages of compact structure, small volume and the like, and a larger reduction ratio can be obtained through reasonable design, so that the planetary transmission is widely applied to various transmissions. The functioning of the planetary transmission depends on the combination of the planetary rows, in particular the selection of the planetary row connections, the position arrangement of the power transmission components, so that the overall planetary transmission has different characteristics. Therefore, it is a problem to be solved by those skilled in the art to improve a planetary gear train to make a transmission mechanism have more gears, higher efficiency and better reliability so as to meet the requirements of durability, dynamic property and the like of a vehicle.
Disclosure of Invention
Technical problem to be solved
The technical problem to be solved by the invention is as follows: how to provide a planetary transmission mechanism with seven forward gears and three reverse gears, which are ten gears, can remarkably improve the dynamic property and the fuel economy of a vehicle.
(II) technical scheme
In order to solve the technical problem, the invention provides a four-degree-of-freedom multi-gear planetary speed change mechanism for a tracked vehicle, which comprises: the four planet rows are arranged on an input member I and an output member II, two ends of which are respectively connected with the input shaft and the output shaft, six transmission members, three clutches and three brakes;
the four planet rows are a planet row PGS1, a planet row PGS2, a planet row PGS3 and a planet row PGS4 respectively;
the planet row PGS1 comprises a row of planet carriers CA1, a row of ring gears R1, a row of sun gears S1 and a row of planet gears; the planet row PGS2 comprises a double-row planet carrier CA2, a double-row ring gear R2, a double-row sun gear S2 and double-row planet gears; the planet row PGS3 comprises a three-row planet carrier CA3, a three-row ring gear R3, a three-row sun gear S3 and three rows of planet gears; the planet row PGS4 comprises a four-row planet carrier CA4, a four-row ring gear R4, a four-row sun gear S4 and four-row planet gears;
the six transmission components are respectively a transmission component (c), a transmission component (c) and a transmission component (b);
the three clutches are a clutch C1, a clutch C2 and a clutch C3 respectively;
the three brakes are respectively a brake B1, a brake B2 and a brake B3;
wherein the input member (r) is connected to the three row carrier CA3 of the planetary row PGS 3;
the transmission member (c) is respectively connected with the three-row sun gear S3 of the planet row PGS3, the four-row sun gear S4 of the planet row PGS4 and the inner hub of the three-row brake B3;
the transmission member (IV) is respectively connected with a three-row ring gear R3 of the planet row PGS3, a four-row planet carrier CA4 of the planet row PGS4 and an inner hub of a brake B2;
the transmission component (c) is respectively connected with a row of planet carriers CA1 of the planet row PGS1, a second row of ring gears R2 of the planet row PGS2 and a fourth row of ring gears R4 of the planet row PGS 4;
the transmission member is connected with a row of ring gears R1 of the planet row PGS1, a two-row planet carrier CA2 of the planet row PGS2 and an inner hub of a clutch C3 respectively;
the transmission component is respectively connected with a second-row sun gear S2 of the planetary row PGS2 and an inner hub of the clutch C1;
the transmission component (B) is respectively connected with a row of sun gears (S1) of a planet row PGS1 and an inner hub of a brake (B1);
the output member (C) connects the outer hub of clutch C1 and the outer hub of clutch C2;
the brake B1 is used for braking the transmission component (B);
the brake B2 is used for braking a transmission component (r);
the brake B3 is used for braking a transmission component (c);
the clutch C1 is used for connecting an output component II and a transmission component III;
the clutch C2 is used for connecting an output member II and a transmission member IV;
the clutch C3 is used to connect the output member and the driving member.
The six transmission components connect basic components of each planetary row with the input shaft and the output shaft to realize the required speed change control.
The planetary speed change mechanism is suitable for an automatic transmission of a vehicle using an engine or a motor as a power source.
The planetary rows are arranged in sequence, the planetary rows are connected by a transmission component, an input shaft is connected with an input component I, and the power output by a power source is transmitted to the speed change mechanism; the output shaft is connected with the output member II, and power is transmitted to the front and rear axles or the left and right driving wheels through a transfer case or a differential.
In the planetary row PGS1, a row of planet gears are externally meshed with a row of sun gears S1 and internally meshed with a row of ring gears R1, and a row of planet carriers CA1 support a row of planet gears;
the planetary row PGS2, the planetary row PGS3 and the planetary row PGS4 are engaged and supported in the same manner as the planetary row PGS 1.
The automatic speed change mechanism is used for realizing seven forward gears and three reverse gears; the seven forward gears are respectively marked as: d1, D2, D3, D4, D5, D6 and D7, and the three reverse gears are respectively marked as R1, R2 and R3.
Wherein, the automatic transmission mechanism realizes the process of forward gear:
(1) the D1 gear is realized by combining the brake B1, the brake B3 and the clutch C1:
in combination with the brake B1, the rotating speed of the sun gear S1 in one row is zero; the rotation speed of the three-row sun gear S3 and the four-row sun gear S4 is zero by combining the brake B3; the second row sun gear S2 is connected with the clutch C1, and the rotating speed of the transmission component II is the same.
The power is input and transmitted to a three-row planet carrier CA3 through an input shaft I, is internally meshed with three rows of planet gears R3 through a three-row planet gear and transmission component II, is transmitted to a four-row planet carrier CA4, is internally meshed with four rows of planet gears through a four-row ring gear R4 and transmission component II, is transmitted to a one-row planet carrier CA1 and a two-row ring gear R2, is transmitted to a two-row planet carrier CA2 through a one-row ring gear R1 and one-row planet gear internally meshed with the transmission component II, is externally meshed with a two-row sun gear S2 through a two-row planet gear and is output to an output component II through a two-row sun gear S2 to realize D1 gear;
(2) the D2 gear is realized by combining the brake B1, the brake B3 and the clutch C3:
in combination with the brake B1, the rotating speed of the sun gear S1 in one row is zero; the rotation speed of the three-row sun gear S3 and the four-row sun gear S4 is zero by combining the brake B3; and in combination with the clutch C3, the one-row ring gear R1, the two-row planet carrier CA2 and the transmission member (II) have the same rotating speed.
The power is input and transmitted to a three-row planet carrier CA3 through an input shaft, is transmitted to a four-row planet carrier CA4 through the inner meshing and transmission component of three-row planet gears and a three-row gear ring R3, is transmitted to a four-row planet carrier CA4 through the inner meshing and transmission component of a four-row gear ring R4 and a four-row planet gear ring, is transmitted to a row of planet carrier CA1 and a two-row gear ring R2, and is transmitted to a row of gear ring R1 and an output component through the inner meshing of a row of gear ring R1 and a row of planet gears, so that the D2 gear is realized.
(3) The D3 gear is realized by combining the brake B3, the clutch C1 and the clutch C3:
the rotation speed of the three-row sun gear S3 and the four-row sun gear S4 is zero by combining the brake B3; the second-row sun gear S2 has the same rotating speed as the transmission component II by combining the brake C1; the combination of the clutch C3, a row of gear rings R1, a double-row planet carrier CA2 and a transmission member II have the same rotating speed;
the power is input and transmitted to a three-row planet carrier CA3 through an input shaft, is transmitted to a four-row planet carrier CA4 through the inner meshing of three rows of planet gears and a three-row gear ring R3 and a transmission component, is transmitted to a row of planet carrier CA1 through the inner meshing of a four-row gear ring R4 and a four-row planet gear and a transmission component, and is transmitted to a row of planet carrier R1 and an output component through the inner meshing of a row of ring gear R1 and a row of planet gears, so that D3 gear is realized.
(4) The D4 gear is realized by combining the brake B3, the clutch C1 and the clutch C2:
the rotation speed of the three-row sun gear S3 and the four-row sun gear S4 is zero by combining the brake B3; the second-row sun gear S2 and the transmission member II have the same rotating speed by combining the clutch C1; the combination clutch C2, the three-row gear ring R3, the four-row planet carrier CA4 and the transmission member II have the same rotating speed;
the power is input and transmitted to a three-row planet carrier CA3 through an input shaft I, and is internally meshed with a three-row gear ring R3 through three rows of planet wheels to be output to an output member II to realize a D4 gear;
(5) the D5 gear is realized by combining the clutch C1, the clutch C2 and the clutch C3:
the second-row sun gear S2 and the output member II have the same rotating speed by combining the clutch C1; the combination clutch C2, the three-row gear ring R3, the four-row planet carrier CA4 and the output member II have the same rotating speed; the combination of the clutch C3, a row of ring gears R1, a double-row planet carrier CA2 and an output member II have the same rotating speed;
power is input and transmitted to the three-row planet carrier CA3 through the input shaft I, and is internally meshed with the three-row ring gear R3 through the three-row planet gears to be output to the output member II, so that the D5 gear is realized.
(6) The D6 gear is realized by combining the brake B1, the clutch C2 and the clutch C3:
in combination with the brake B1, the rotating speed of the sun gear S1 in one row is zero; the combination clutch C2, the three-row gear ring R3, the four-row planet carrier CA4 and the output member II have the same rotating speed; the combination of the clutch C3, a row of ring gears R1, a double-row planet carrier CA2 and an output member II have the same rotating speed;
the power is input and transmitted to a three-row planet carrier CA3 through an input shaft I, and is internally meshed with a three-row gear ring R3 through three rows of planet wheels to be output to an output member II to realize a D6 gear;
(7) the D7 gear is realized by combining the brake B1, the clutch C1 and the clutch C2:
in combination with the brake B1, the rotating speed of the sun gear S1 in one row is zero; the second-row sun gear S2 and the output member II have the same rotating speed by combining the clutch C1; the combination clutch C2, the three-row gear ring R3, the four-row planet carrier CA4 and the output member II have the same rotating speed;
power is input and transmitted to the three-row planet carrier CA3 through the input shaft I, and is internally meshed with the three-row ring gear R3 through the three-row planet gears to be output to the output member II, so that the D7 gear is realized.
Wherein, the automatic transmission mechanism realizes the process of reverse gear:
(8) the R1 gear is realized by combining the brake B1, the brake B2 and the clutch C1:
in combination with the brake B1, the rotating speed of the sun gear S1 in one row is zero; in combination with the brake B2, the rotating speed of the four-row planet carrier CA4 and the three-row gear ring R3 is zero; the second-row sun gear S2 and the output member II have the same rotating speed by combining the clutch C1;
the power is input through an input shaft I and transmitted to a three-row planet carrier CA3, is externally engaged with a three-row sun gear S3 through a three-row planet gear, is transmitted to a four-row gear ring R4 through a transmission member III, is transmitted to a one-row planet carrier CA1 and a two-row gear ring R2 through a transmission member V, is internally engaged with a one-row planet gear through a one-row gear ring R1 and is transmitted to a two-row planet carrier CA2 through a transmission member IV, is externally engaged with a two-row sun gear S2 through a two-row planet gear, and is output to an output member through a two-row sun gear S2 to realize R1 gear;
(9) the R2 gear is realized by combining the brake B1, the brake B2 and the clutch C3:
in combination with the brake B1, the rotating speed of the sun gear S1 in one row is zero; in combination with the brake B2, the rotating speed of the four-row planet carrier CA4 and the three-row gear ring R3 is zero; the combination of the clutch C3, a row of gear rings R1, a double-row planet carrier CA2 and a transmission member II have the same rotating speed;
the power is input and transmitted to a three-row planet carrier CA3 through an input shaft I, is externally engaged with a three-row sun gear S3 through three rows of planet gears, is transmitted to a four-row gear ring R4 through a transmission component III and four rows of engagement, is transmitted to a row of planet carrier CA1 and a two-row gear ring R2 through a transmission component V, and is internally engaged with a row of planet gears through a row of gear ring R1 and is transmitted to a row of gear ring R1 and an output component II to realize R2 gear;
(10) the R3 gear is realized by combining the brake B2, the clutch C1 and the clutch C3:
in combination with the brake B2, the rotating speed of the four-row planet carrier CA4 and the three-row gear ring R3 is zero; the second-row sun gear S2 and the transmission member II have the same rotating speed by combining the clutch C1; the combination of the clutch C3, a row of gear rings R1, a double-row planet carrier CA2 and a transmission member II have the same rotating speed;
the power is input and transmitted to a three-row planet carrier CA3 through an input shaft I, is externally engaged with a three-row sun gear S3 through three rows of planet gears, is transmitted to a four-row gear ring R4 through a transmission member III and four rows of engagement, is transmitted to a row of planet carrier CA1 and a two-row gear ring R2 through a transmission member V, and is transmitted to a row of gear ring R1 and an output member II through the inner engagement of a row of gear ring R1 and a row of planet gears, so that the R3 gear is realized.
(III) advantageous effects
Compared with the prior art, the four-degree-of-freedom multi-gear planetary speed change mechanism for the tracked vehicle is simple and reliable in structural form by adopting simple planetary row connection, improves the reliability and durability of the gearbox, and enables the gearbox to be easily disassembled and maintained. Meanwhile, the characteristic that the seven-first-three-reverse speed change mechanism has ten gears ensures that the vehicle has good dynamic property and transmission efficiency.
Drawings
FIG. 1 is a diagrammatic view of the drive of the present invention;
in the figure: PGS1, PGS2, PGS3, PGS4 are simple planetary rows, the first is input member, the second is output member, the third, fourth, fifth, sixth, seventh and eighth are six basic transmission members, the first is driving member, the second is driven member, B1, B2, B3 are three brakes, C1, C2 and C3 are three clutches.
Wherein, R1 is a row of gear rings, CA1 is a row of planet carriers, and S1 is a row of sun gears; r2 is a two-row gear ring, CA2 is a two-row planet carrier, and S2 is a two-row sun gear; r3 is a three-row gear ring, CA3 is a three-row planet carrier, and S3 is a three-row sun gear; r4 is a four-row ring gear, CA4 is a four-row planet carrier, and S4 is a four-row sun gear.
Detailed Description
In order to make the objects, contents, and advantages of the present invention clearer, the following detailed description of the embodiments of the present invention will be made in conjunction with the accompanying drawings and examples.
In order to solve the problems of the prior art, the invention provides a four-degree-of-freedom multi-gear planetary speed change mechanism for a tracked vehicle, as shown in fig. 1, comprising: the four planet rows are arranged on an input member I and an output member II, two ends of which are respectively connected with the input shaft and the output shaft, six transmission members, three clutches and three brakes;
the four planet rows are a planet row PGS1, a planet row PGS2, a planet row PGS3 and a planet row PGS4 respectively;
the planet row PGS1 comprises a row of planet carriers CA1, a row of ring gears R1, a row of sun gears S1 and a row of planet gears; the planet row PGS2 comprises a double-row planet carrier CA2, a double-row ring gear R2, a double-row sun gear S2 and double-row planet gears; the planet row PGS3 comprises a three-row planet carrier CA3, a three-row ring gear R3, a three-row sun gear S3 and three rows of planet gears; the planet row PGS4 comprises a four-row planet carrier CA4, a four-row ring gear R4, a four-row sun gear S4 and four-row planet gears;
the six transmission components are respectively a transmission component (c), a transmission component (c) and a transmission component (b);
the three clutches are a clutch C1, a clutch C2 and a clutch C3 respectively;
the three brakes are respectively a brake B1, a brake B2 and a brake B3;
the planet row PGS1 is respectively connected with a fifth transmission component, a sixth transmission component and a eighth transmission component;
the planet row PGS2 is respectively connected with a transmission member (c), a transmission member (c) and a transmission member (c);
the planet row PGS3 is respectively connected with an input component (I), a transmission component (III) and a transmission component (IV);
the planet row PGS4 is respectively connected with the transmission member (c), the transmission member (c) and the transmission member (c);
wherein the input member (r) is connected to the three row carrier CA3 of the planetary row PGS 3;
the transmission member (c) is respectively connected with the three-row sun gear S3 of the planet row PGS3, the four-row sun gear S4 of the planet row PGS4 and the inner hub of the three-row brake B3;
the transmission member (IV) is respectively connected with a three-row ring gear R3 of the planet row PGS3, a four-row planet carrier CA4 of the planet row PGS4 and an inner hub of a brake B2;
the transmission component (c) is respectively connected with a row of planet carriers CA1 of the planet row PGS1, a second row of ring gears R2 of the planet row PGS2 and a fourth row of ring gears R4 of the planet row PGS 4;
the transmission member is connected with a row of ring gears R1 of the planet row PGS1, a two-row planet carrier CA2 of the planet row PGS2 and an inner hub of a clutch C3 respectively;
the transmission component is respectively connected with a second-row sun gear S2 of the planetary row PGS2 and an inner hub of the clutch C1;
the transmission component (B) is respectively connected with a row of sun gears (S1) of a planet row PGS1 and an inner hub of a brake (B1);
the output member (C) connects the outer hub of clutch C1 and the outer hub of clutch C2;
the brake B1 is used for braking the transmission component (B);
the brake B2 is used for braking a transmission component (r);
the brake B3 is used for braking a transmission component (c);
the clutch C1 is used for connecting an output component II and a transmission component III;
the clutch C2 is used for connecting an output member II and a transmission member IV;
the clutch C3 is used to connect the output member and the driving member.
The six transmission components connect basic components of each planetary row with the input shaft and the output shaft to realize the required speed change control.
The planetary speed change mechanism is suitable for an automatic transmission of a vehicle using an engine or a motor as a power source.
The planetary rows are arranged in sequence, the planetary rows are connected by a transmission component, an input shaft is connected with an input component I, and the power output by a power source is transmitted to the speed change mechanism; the output shaft is connected with the output member II, and power is transmitted to the front and rear axles or the left and right driving wheels through a transfer case or a differential.
In the planetary row PGS1, a row of planet gears are externally meshed with a row of sun gears S1 and internally meshed with a row of ring gears R1, and a row of planet carriers CA1 support a row of planet gears;
the planetary row PGS2, the planetary row PGS3 and the planetary row PGS4 are engaged and supported in the same manner as the planetary row PGS 1.
The automatic speed change mechanism is used for realizing seven forward gears and three reverse gears; the seven forward gears are respectively marked as: d1, D2, D3, D4, D5, D6 and D7, and the three reverse gears are respectively marked as R1, R2 and R3.
Wherein, the automatic transmission mechanism realizes the process of forward gear:
(1) the D1 gear is realized by combining the brake B1, the brake B3 and the clutch C1:
in combination with the brake B1, the rotating speed of the sun gear S1 in one row is zero; the rotation speed of the three-row sun gear S3 and the four-row sun gear S4 is zero by combining the brake B3; the second row sun gear S2 is connected with the clutch C1, and the rotating speed of the transmission component II is the same.
The power is input and transmitted to a three-row planet carrier CA3 through an input shaft I, is internally meshed with three rows of planet gears R3 through a three-row planet gear and transmission component II, is transmitted to a four-row planet carrier CA4, is internally meshed with four rows of planet gears through a four-row ring gear R4 and transmission component II, is transmitted to a one-row planet carrier CA1 and a two-row ring gear R2, is transmitted to a two-row planet carrier CA2 through a one-row ring gear R1 and one-row planet gear internally meshed with the transmission component II, is externally meshed with a two-row sun gear S2 through a two-row planet gear and is output to an output component II through a two-row sun gear S2 to realize D1 gear;
(2) the D2 gear is realized by combining the brake B1, the brake B3 and the clutch C3:
in combination with the brake B1, the rotating speed of the sun gear S1 in one row is zero; the rotation speed of the three-row sun gear S3 and the four-row sun gear S4 is zero by combining the brake B3; and in combination with the clutch C3, the one-row ring gear R1, the two-row planet carrier CA2 and the transmission member (II) have the same rotating speed.
The power is input and transmitted to a three-row planet carrier CA3 through an input shaft, is transmitted to a four-row planet carrier CA4 through the inner meshing and transmission component of three-row planet gears and a three-row gear ring R3, is transmitted to a four-row planet carrier CA4 through the inner meshing and transmission component of a four-row gear ring R4 and a four-row planet gear ring, is transmitted to a row of planet carrier CA1 and a two-row gear ring R2, and is transmitted to a row of gear ring R1 and an output component through the inner meshing of a row of gear ring R1 and a row of planet gears, so that the D2 gear is realized.
(3) The D3 gear is realized by combining the brake B3, the clutch C1 and the clutch C3:
the rotation speed of the three-row sun gear S3 and the four-row sun gear S4 is zero by combining the brake B3; the second-row sun gear S2 has the same rotating speed as the transmission component II by combining the brake C1; the combination of the clutch C3, a row of gear rings R1, a double-row planet carrier CA2 and a transmission member II have the same rotating speed;
the power is input and transmitted to a three-row planet carrier CA3 through an input shaft, is transmitted to a four-row planet carrier CA4 through the inner meshing of three rows of planet gears and a three-row gear ring R3 and a transmission component, is transmitted to a row of planet carrier CA1 through the inner meshing of a four-row gear ring R4 and a four-row planet gear and a transmission component, and is transmitted to a row of planet carrier R1 and an output component through the inner meshing of a row of ring gear R1 and a row of planet gears, so that D3 gear is realized.
(4) The D4 gear is realized by combining the brake B3, the clutch C1 and the clutch C2:
the rotation speed of the three-row sun gear S3 and the four-row sun gear S4 is zero by combining the brake B3; the second-row sun gear S2 and the transmission member II have the same rotating speed by combining the clutch C1; the combination clutch C2, the three-row gear ring R3, the four-row planet carrier CA4 and the transmission member II have the same rotating speed;
the power is input and transmitted to a three-row planet carrier CA3 through an input shaft I, and is internally meshed with a three-row gear ring R3 through three rows of planet wheels to be output to an output member II to realize a D4 gear;
(5) the D5 gear is realized by combining the clutch C1, the clutch C2 and the clutch C3:
the second-row sun gear S2 and the output member II have the same rotating speed by combining the clutch C1; the combination clutch C2, the three-row gear ring R3, the four-row planet carrier CA4 and the output member II have the same rotating speed; the combination of the clutch C3, a row of ring gears R1, a double-row planet carrier CA2 and an output member II have the same rotating speed;
power is input and transmitted to the three-row planet carrier CA3 through the input shaft I, and is internally meshed with the three-row ring gear R3 through the three-row planet gears to be output to the output member II, so that the D5 gear is realized.
(6) The D6 gear is realized by combining the brake B1, the clutch C2 and the clutch C3:
in combination with the brake B1, the rotating speed of the sun gear S1 in one row is zero; the combination clutch C2, the three-row gear ring R3, the four-row planet carrier CA4 and the output member II have the same rotating speed; the combination of the clutch C3, a row of ring gears R1, a double-row planet carrier CA2 and an output member II have the same rotating speed;
the power is input and transmitted to a three-row planet carrier CA3 through an input shaft I, and is internally meshed with a three-row gear ring R3 through three rows of planet wheels to be output to an output member II to realize a D6 gear;
(7) the D7 gear is realized by combining the brake B1, the clutch C1 and the clutch C2:
in combination with the brake B1, the rotating speed of the sun gear S1 in one row is zero; the second-row sun gear S2 and the output member II have the same rotating speed by combining the clutch C1; the combination clutch C2, the three-row gear ring R3, the four-row planet carrier CA4 and the output member II have the same rotating speed;
power is input and transmitted to the three-row planet carrier CA3 through the input shaft I, and is internally meshed with the three-row ring gear R3 through the three-row planet gears to be output to the output member II, so that the D7 gear is realized.
Wherein, the automatic transmission mechanism realizes the process of reverse gear:
(8) the R1 gear is realized by combining the brake B1, the brake B2 and the clutch C1:
in combination with the brake B1, the rotating speed of the sun gear S1 in one row is zero; in combination with the brake B2, the rotating speed of the four-row planet carrier CA4 and the three-row gear ring R3 is zero; the second-row sun gear S2 and the output member II have the same rotating speed by combining the clutch C1;
the power is input through an input shaft I and transmitted to a three-row planet carrier CA3, is externally engaged with a three-row sun gear S3 through a three-row planet gear, is transmitted to a four-row gear ring R4 through a transmission member III, is transmitted to a one-row planet carrier CA1 and a two-row gear ring R2 through a transmission member V, is internally engaged with a one-row planet gear through a one-row gear ring R1 and is transmitted to a two-row planet carrier CA2 through a transmission member IV, is externally engaged with a two-row sun gear S2 through a two-row planet gear, and is output to an output member through a two-row sun gear S2 to realize R1 gear;
(9) the R2 gear is realized by combining the brake B1, the brake B2 and the clutch C3:
in combination with the brake B1, the rotating speed of the sun gear S1 in one row is zero; in combination with the brake B2, the rotating speed of the four-row planet carrier CA4 and the three-row gear ring R3 is zero; the combination of the clutch C3, a row of gear rings R1, a double-row planet carrier CA2 and a transmission member II have the same rotating speed;
the power is input and transmitted to a three-row planet carrier CA3 through an input shaft I, is externally engaged with a three-row sun gear S3 through three rows of planet gears, is transmitted to a four-row gear ring R4 through a transmission component III and four rows of engagement, is transmitted to a row of planet carrier CA1 and a two-row gear ring R2 through a transmission component V, and is internally engaged with a row of planet gears through a row of gear ring R1 and is transmitted to a row of gear ring R1 and an output component II to realize R2 gear;
(10) the R3 gear is realized by combining the brake B2, the clutch C1 and the clutch C3:
in combination with the brake B2, the rotating speed of the four-row planet carrier CA4 and the three-row gear ring R3 is zero; the second-row sun gear S2 and the transmission member II have the same rotating speed by combining the clutch C1; the combination of the clutch C3, a row of gear rings R1, a double-row planet carrier CA2 and a transmission member II have the same rotating speed;
the power is input and transmitted to a three-row planet carrier CA3 through an input shaft I, is externally engaged with a three-row sun gear S3 through three rows of planet gears, is transmitted to a four-row gear ring R4 through a transmission member III and four rows of engagement, is transmitted to a row of planet carrier CA1 and a two-row gear ring R2 through a transmission member V, and is transmitted to a row of gear ring R1 and an output member II through the inner engagement of a row of gear ring R1 and a row of planet gears, so that the R3 gear is realized.
Example 1
As shown in fig. 1, the planetary transmission mechanism of the present embodiment is applied to a vehicle automatic transmission that uses an engine or a motor as a power source. The planetary rows are arranged in sequence, the planetary rows are connected by a transmission member, and an input shaft is connected with an input member (I) and transmits the power output by a power source to the planetary speed change mechanism. The output shaft is connected with the output member II, and power is transmitted to the front and rear axles or the left and right driving wheels through a transfer case or a differential.
The planet row PGS1 is a simple planet row and comprises a row of planet carriers CA1, a row of gear rings R1, a row of sun gears S1 and a row of planet gears, wherein the row of planet gears are externally meshed with the row of sun gears S1 and internally meshed with the row of gear rings, and the row of planet carriers CA1 supports the row of planet gears.
The planetary rows PGS2, PGS3, PGS4 mesh and support in the same manner as PGS 1.
For a simple planet row, the characteristic parameter k is the ratio between the product of the tooth number of the ring gear and the tooth number of the meshing planet gear and the product of the tooth number of the sun gear and the tooth number of the meshing planet gear, and the characteristic parameters of the four planet rows in fig. 1 are respectively: k 1-1.58, k 2-1.82, k 3-2.81, and k 4-1.83.
The following is a description of the implementation of each gear, and the seven forward gears implemented by this transmission mechanism are respectively labeled: d1, D2, D3, D4, D5, D6, D7, three reverse gears being respectively marked R1, R2, R3: because this derailleur is four degree of freedom derailleurs, realize that certain gear needs three control pieces of action, eliminate another three degrees of freedom, can realize fixed input and output, now analyze as follows:
(1) the D1 gear is realized by combining the brake B1, the brake B3 and the clutch C1:
in combination with the brake B1, the rotating speed of the sun gear S1 in one row is zero; the rotation speed of the three-row sun gear S3 and the four-row sun gear S4 is zero by combining the brake B3; the second row sun gear S2 is connected with the clutch C1, and the rotating speed of the transmission component II is the same.
The power is input through an input shaft I and transmitted to a three-row planet carrier CA3, is transmitted to a four-row planet carrier CA4 through inner meshing and transmission components of three-row planet gears and three-row gear rings R3, is transmitted to a four-row planet carrier CA 3526, is transmitted to a one-row planet carrier CA1 and a two-row gear ring R2 through inner meshing and transmission components of the four-row gear rings R4 and the four-row planet gears, is transmitted to a two-row planet carrier CA2 through inner meshing of the one-row gear rings R1 and the one-row planet gears, is externally meshed with a two-row sun gear S2 through the two-row planet gear and is output to an output component through a two-row sun gear S2 to realize D1 gear.
(2) The D2 gear is realized by combining the brake B1, the brake B3 and the clutch C3:
in combination with the brake B1, the rotating speed of the sun gear S1 in one row is zero; the rotation speed of the three-row sun gear S3 and the four-row sun gear S4 is zero by combining the brake B3; and in combination with the clutch C3, the one-row ring gear R1, the two-row planet carrier CA2 and the transmission member (II) have the same rotating speed.
The power is input and transmitted to a three-row planet carrier CA3 through an input shaft, is transmitted to a four-row planet carrier CA4 through the inner meshing and transmission component of three-row planet gears and a three-row gear ring R3, is transmitted to a four-row planet carrier CA4 through the inner meshing and transmission component of a four-row gear ring R4 and a four-row planet gear ring, is transmitted to a row of planet carrier CA1 and a two-row gear ring R2, and is transmitted to a row of gear ring R1 and an output component through the inner meshing of a row of gear ring R1 and a row of planet gears, so that the D2 gear is realized.
(3) The D3 gear is realized by combining the brake B3, the clutch C1 and the clutch C3:
the rotation speed of the three-row sun gear S3 and the four-row sun gear S4 is zero by combining the brake B3; the second-row sun gear S2 has the same rotating speed as the transmission component II by combining the brake C1; and in combination with the clutch C3, the one-row ring gear R1, the two-row planet carrier CA2 and the transmission member (II) have the same rotating speed.
The power is input and transmitted to a three-row planet carrier CA3 through an input shaft, is transmitted to a four-row planet carrier CA4 through the inner meshing of three rows of planet gears and a three-row gear ring R3 and a transmission component, is transmitted to a row of planet carrier CA1 through the inner meshing of a four-row gear ring R4 and a four-row planet gear and a transmission component, and is transmitted to a row of planet carrier R1 and an output component through the inner meshing of a row of ring gear R1 and a row of planet gears, so that D3 gear is realized.
(4) The D4 gear is realized by combining the brake B3, the clutch C1 and the clutch C2:
the rotation speed of the three-row sun gear S3 and the four-row sun gear S4 is zero by combining the brake B3; the second-row sun gear S2 and the transmission member II have the same rotating speed by combining the clutch C1; and in combination with the clutch C2, the three-row gear ring R3, the four-row planet carrier CA4 and the transmission member (II) have the same rotating speed.
Power is input and transmitted to the three-row planet carrier CA3 through the input shaft I, and is internally meshed with the three-row ring gear R3 through the three-row planet gears to be output to the output member II, so that the D4 gear is realized.
(5) The D5 gear is realized by combining the clutch C1, the clutch C2 and the clutch C3:
the second-row sun gear S2 and the transmission member II have the same rotating speed by combining the clutch C1; the combination clutch C2, the three-row gear ring R3, the four-row planet carrier CA4 and the transmission member II have the same rotating speed; and in combination with the clutch C3, the one-row ring gear R1, the two-row planet carrier CA2 and the transmission member (II) have the same rotating speed.
Power is input and transmitted to the three-row planet carrier CA3 through the input shaft I, and is internally meshed with the three-row ring gear R3 through the three-row planet gears to be output to the output member II, so that the D5 gear is realized.
(6) The D6 gear is realized by combining the brake B1, the clutch C2 and the clutch C3:
in combination with the brake B1, the rotating speed of the sun gear S1 in one row is zero; the combination clutch C2, the three-row gear ring R3, the four-row planet carrier CA4 and the transmission member II have the same rotating speed; and in combination with the clutch C3, the one-row ring gear R1, the two-row planet carrier CA2 and the transmission member (II) have the same rotating speed.
Power is input and transmitted to the three-row planet carrier CA3 through the input shaft I, and is internally meshed with the three-row ring gear R3 through the three-row planet gears to be output to the output member II, so that the D6 gear is realized.
(7) The D7 gear is realized by combining the brake B1, the clutch C1 and the clutch C2:
in combination with the brake B1, the rotating speed of the sun gear S1 in one row is zero; the second-row sun gear S2 and the transmission member II have the same rotating speed by combining the clutch C1; and in combination with the clutch C2, the three-row gear ring R3, the four-row planet carrier CA4 and the transmission member (II) have the same rotating speed.
Power is input and transmitted to the three-row planet carrier CA3 through the input shaft I, and is internally meshed with the three-row ring gear R3 through the three-row planet gears to be output to the output member II, so that the D7 gear is realized.
(8) The R1 gear is realized by combining the brake B1, the brake B2 and the clutch C1:
in combination with the brake B1, the rotating speed of the sun gear S1 in one row is zero; in combination with the brake B2, the rotating speed of the four-row planet carrier CA4 and the three-row gear ring R3 is zero; the second row sun gear S2 is connected with the clutch C1, and the rotating speed of the transmission component II is the same.
The power is transmitted to a three-row planet carrier CA3 through an input shaft I, is transmitted to a four-row gear ring R4 through the external meshing of three rows of planet gears and a three-row sun gear S3, a transmission component III and the four-row meshing, is transmitted to a one-row planet carrier CA1 and a two-row gear ring R2 through a transmission component V, is transmitted to a two-row planet carrier CA2 through the internal meshing of the one-row gear ring R1 and the one-row planet gears, is transmitted to the two-row sun gear S2 through the external meshing of the two-row planet gears and is output to an output component through the two-row sun gear S2, and R1 gear is realized.
(9) The R2 gear is realized by combining the brake B1, the brake B2 and the clutch C3:
in combination with the brake B1, the rotating speed of the sun gear S1 in one row is zero; in combination with the brake B2, the rotating speed of the four-row planet carrier CA4 and the three-row gear ring R3 is zero; and in combination with the clutch C3, the one-row ring gear R1, the two-row planet carrier CA2 and the transmission member (II) have the same rotating speed.
The power is input and transmitted to a three-row planet carrier CA3 through an input shaft I, is externally engaged with a three-row sun gear S3 through three rows of planet gears, is transmitted to a four-row gear ring R4 through a transmission member III and four rows of engagement, is transmitted to a row of planet carrier CA1 and a two-row gear ring R2 through a transmission member V, and is transmitted to a row of gear ring R1 and an output member II through the inner engagement of a row of gear ring R1 and a row of planet gears, so that the R2 gear is realized.
(10) The R3 gear is realized by combining the brake B2, the clutch C1 and the clutch C3:
in combination with the brake B2, the rotating speed of the four-row planet carrier CA4 and the three-row gear ring R3 is zero; the second-row sun gear S2 and the transmission member II have the same rotating speed by combining the clutch C1; and in combination with the clutch C3, the one-row ring gear R1, the two-row planet carrier CA2 and the transmission member (II) have the same rotating speed.
The power is input and transmitted to a three-row planet carrier CA3 through an input shaft I, is externally engaged with a three-row sun gear S3 through three rows of planet gears, is transmitted to a four-row gear ring R4 through a transmission member III and four rows of engagement, is transmitted to a row of planet carrier CA1 and a two-row gear ring R2 through a transmission member V, and is transmitted to a row of gear ring R1 and an output member II through the inner engagement of a row of gear ring R1 and a row of planet gears, so that the R3 gear is realized.
Table 1 shows the planetary transmission gears and ratios, which describes the operating members that need to be engaged to achieve each gear, and also gives the step ratios between the gears
TABLE 1 operating member combination sequence and transmission ratio for realizing each gear
Gear position Shift logic Transmission ratio Step ratio
1 [B1、B3、C1] 5.8391 1.7054
2 [B1、B3、C3] 3.4239 1.7054
3 [B3、C1、C3] 2.0968 1.7054
4 [B3、C1、C2] 1.3559 1.7054
5 [C1、C2、B3] 1.0 1.7054
6 [B1、C2、C3] 0.8431 1.7054
7 [B1、C1、C2] 0.7646 1.7054
R1 [B1、B2、C1] -5.7979 1.7054
R2 [B1、B2、C3] -3.3997 1.7054
R3 [B2、C1、C3] -2.0820 1.7054
The above description is only a preferred embodiment of the present invention, and it should be noted that, for those skilled in the art, several modifications and variations can be made without departing from the technical principle of the present invention, and these modifications and variations should also be regarded as the protection scope of the present invention.

Claims (10)

1. A four-degree-of-freedom multi-gear planetary speed change mechanism for a tracked vehicle is characterized by comprising: the four planet rows are arranged on an input member I and an output member II, two ends of which are respectively connected with the input shaft and the output shaft, six transmission members, three clutches and three brakes;
the four planet rows are a planet row PGS1, a planet row PGS2, a planet row PGS3 and a planet row PGS4 respectively;
the planet row PGS1 comprises a row of planet carriers CA1, a row of ring gears R1, a row of sun gears S1 and a row of planet gears; the planet row PGS2 comprises a double-row planet carrier CA2, a double-row ring gear R2, a double-row sun gear S2 and double-row planet gears; the planet row PGS3 comprises a three-row planet carrier CA3, a three-row ring gear R3, a three-row sun gear S3 and three rows of planet gears; the planet row PGS4 comprises a four-row planet carrier CA4, a four-row ring gear R4, a four-row sun gear S4 and four-row planet gears;
the six transmission components are respectively a transmission component (c), a transmission component (c) and a transmission component (b);
the three clutches are a clutch C1, a clutch C2 and a clutch C3 respectively;
the three brakes are respectively a brake B1, a brake B2 and a brake B3;
wherein the input member (r) is connected to the three row carrier CA3 of the planetary row PGS 3;
the transmission member (c) is respectively connected with the three-row sun gear S3 of the planet row PGS3, the four-row sun gear S4 of the planet row PGS4 and the inner hub of the three-row brake B3;
the transmission member (IV) is respectively connected with a three-row ring gear R3 of the planet row PGS3, a four-row planet carrier CA4 of the planet row PGS4 and an inner hub of a brake B2;
the transmission component (c) is respectively connected with a row of planet carriers CA1 of the planet row PGS1, a second row of ring gears R2 of the planet row PGS2 and a fourth row of ring gears R4 of the planet row PGS 4;
the transmission member is connected with a row of ring gears R1 of the planet row PGS1, a two-row planet carrier CA2 of the planet row PGS2 and an inner hub of a clutch C3 respectively;
the transmission component is respectively connected with a second-row sun gear S2 of the planetary row PGS2 and an inner hub of the clutch C1;
the transmission component (B) is respectively connected with a row of sun gears (S1) of a planet row PGS1 and an inner hub of a brake (B1);
the output member (C) connects the outer hub of clutch C1 and the outer hub of clutch C2;
the brake B1 is used for braking the transmission component (B);
the brake B2 is used for braking a transmission component (r);
the brake B3 is used for braking a transmission component (c);
the clutch C1 is used for connecting an output component II and a transmission component III;
the clutch C2 is used for connecting an output member II and a transmission member IV;
the clutch C3 is used to connect the output member and the driving member.
2. The four-degree-of-freedom multi-gear planetary automatic transmission mechanism for the tracked vehicle as claimed in claim 1, wherein the six transmission members connect basic members of each planetary row with the input shaft and the output shaft to realize the required speed change control.
3. The four-degree-of-freedom multi-gear planetary automatic speed change mechanism for the tracked vehicle as claimed in claim 1, wherein the planetary automatic speed change mechanism is suitable for an automatic speed change mechanism of the vehicle which takes an engine or a motor as a power source.
4. The four-degree-of-freedom multi-gear planetary automatic speed change mechanism for the tracked vehicle as claimed in claim 1, wherein the planetary rows are arranged in sequence, the planetary rows are connected by a transmission member, an input shaft is connected with an input member (r), and power output by a power source is transmitted to the speed change mechanism; the output shaft is connected with the output member II, and power is transmitted to the front and rear axles or the left and right driving wheels through a transfer case or a differential.
5. The four-degree-of-freedom multi-gear planetary automatic transmission mechanism for tracked vehicles according to claim 1, wherein in the planetary row PGS1, one row of planet gears is in external engagement with one row of sun gears S1 and is also in internal engagement with one row of ring gears R1, and one row of planet carriers CA1 supports one row of planet gears;
the planetary row PGS2, the planetary row PGS3 and the planetary row PGS4 are engaged and supported in the same manner as the planetary row PGS 1.
6. The four-degree-of-freedom multi-gear planetary automatic transmission mechanism for tracked vehicles according to claim 1, characterized in that it is used to realize seven forward gears and three reverse gears; the seven forward gears are respectively marked as: d1, D2, D3, D4, D5, D6 and D7, and the three reverse gears are respectively marked as R1, R2 and R3.
7. The four-degree-of-freedom multi-gear planetary automatic transmission mechanism for the tracked vehicle as claimed in claim 6, wherein during the implementation of the forward gear of the automatic transmission mechanism:
(1) the D1 gear is realized by combining the brake B1, the brake B3 and the clutch C1:
in combination with the brake B1, the rotating speed of the sun gear S1 in one row is zero; the rotation speed of the three-row sun gear S3 and the four-row sun gear S4 is zero by combining the brake B3; the second row sun gear S2 is connected with the clutch C1, and the rotating speed of the transmission component II is the same.
The power is input and transmitted to a three-row planet carrier CA3 through an input shaft I, is internally meshed with three rows of planet gears R3 through a three-row planet gear and transmission component II, is transmitted to a four-row planet carrier CA4, is internally meshed with four rows of planet gears through a four-row ring gear R4 and transmission component II, is transmitted to a one-row planet carrier CA1 and a two-row ring gear R2, is transmitted to a two-row planet carrier CA2 through a one-row ring gear R1 and one-row planet gear internally meshed with the transmission component II, is externally meshed with a two-row sun gear S2 through a two-row planet gear and is output to an output component II through a two-row sun gear S2 to realize D1 gear;
(2) the D2 gear is realized by combining the brake B1, the brake B3 and the clutch C3:
in combination with the brake B1, the rotating speed of the sun gear S1 in one row is zero; the rotation speed of the three-row sun gear S3 and the four-row sun gear S4 is zero by combining the brake B3; and in combination with the clutch C3, the one-row ring gear R1, the two-row planet carrier CA2 and the transmission member (II) have the same rotating speed.
The power is input and transmitted to a three-row planet carrier CA3 through an input shaft, is transmitted to a four-row planet carrier CA4 through the inner meshing and transmission component of three-row planet gears and a three-row gear ring R3, is transmitted to a four-row planet carrier CA4 through the inner meshing and transmission component of a four-row gear ring R4 and a four-row planet gear ring, is transmitted to a row of planet carrier CA1 and a two-row gear ring R2, and is transmitted to a row of gear ring R1 and an output component through the inner meshing of a row of gear ring R1 and a row of planet gears, so that the D2 gear is realized.
(3) The D3 gear is realized by combining the brake B3, the clutch C1 and the clutch C3:
the rotation speed of the three-row sun gear S3 and the four-row sun gear S4 is zero by combining the brake B3; the second-row sun gear S2 has the same rotating speed as the transmission component II by combining the brake C1; the combination of the clutch C3, a row of gear rings R1, a double-row planet carrier CA2 and a transmission member II have the same rotating speed;
the power is input and transmitted to a three-row planet carrier CA3 through an input shaft, is transmitted to a four-row planet carrier CA4 through the inner meshing of three rows of planet gears and a three-row gear ring R3 and a transmission component, is transmitted to a row of planet carrier CA1 through the inner meshing of a four-row gear ring R4 and a four-row planet gear and a transmission component, and is transmitted to a row of planet carrier R1 and an output component through the inner meshing of a row of ring gear R1 and a row of planet gears, so that D3 gear is realized.
8. The four-degree-of-freedom multi-gear planetary automatic transmission mechanism for the tracked vehicle as claimed in claim 7, wherein during the forward gear implementation of the automatic transmission mechanism:
(4) the D4 gear is realized by combining the brake B3, the clutch C1 and the clutch C2:
the rotation speed of the three-row sun gear S3 and the four-row sun gear S4 is zero by combining the brake B3; the second-row sun gear S2 and the transmission member II have the same rotating speed by combining the clutch C1; the combination clutch C2, the three-row gear ring R3, the four-row planet carrier CA4 and the transmission member II have the same rotating speed;
the power is input and transmitted to a three-row planet carrier CA3 through an input shaft I, and is internally meshed with a three-row gear ring R3 through three rows of planet wheels to be output to an output member II to realize a D4 gear;
(5) the D5 gear is realized by combining the clutch C1, the clutch C2 and the clutch C3:
the second-row sun gear S2 and the output member II have the same rotating speed by combining the clutch C1; the combination clutch C2, the three-row gear ring R3, the four-row planet carrier CA4 and the output member II have the same rotating speed; the combination of the clutch C3, a row of ring gears R1, a double-row planet carrier CA2 and an output member II have the same rotating speed;
power is input and transmitted to the three-row planet carrier CA3 through the input shaft I, and is internally meshed with the three-row ring gear R3 through the three-row planet gears to be output to the output member II, so that the D5 gear is realized.
9. The four-degree-of-freedom multi-gear planetary automatic transmission mechanism for the tracked vehicle as claimed in claim 8, wherein during the forward gear implementation of the automatic transmission mechanism:
(6) the D6 gear is realized by combining the brake B1, the clutch C2 and the clutch C3:
in combination with the brake B1, the rotating speed of the sun gear S1 in one row is zero; the combination clutch C2, the three-row gear ring R3, the four-row planet carrier CA4 and the output member II have the same rotating speed; the combination of the clutch C3, a row of ring gears R1, a double-row planet carrier CA2 and an output member II have the same rotating speed;
the power is input and transmitted to a three-row planet carrier CA3 through an input shaft I, and is internally meshed with a three-row gear ring R3 through three rows of planet wheels to be output to an output member II to realize a D6 gear;
(7) the D7 gear is realized by combining the brake B1, the clutch C1 and the clutch C2:
in combination with the brake B1, the rotating speed of the sun gear S1 in one row is zero; the second-row sun gear S2 and the output member II have the same rotating speed by combining the clutch C1; the combination clutch C2, the three-row gear ring R3, the four-row planet carrier CA4 and the output member II have the same rotating speed;
power is input and transmitted to the three-row planet carrier CA3 through the input shaft I, and is internally meshed with the three-row ring gear R3 through the three-row planet gears to be output to the output member II, so that the D7 gear is realized.
10. The four-degree-of-freedom multi-gear planetary automatic speed change mechanism for the tracked vehicle as claimed in claim 9, wherein during the process of realizing the reverse gear by the automatic speed change mechanism:
(8) the R1 gear is realized by combining the brake B1, the brake B2 and the clutch C1:
in combination with the brake B1, the rotating speed of the sun gear S1 in one row is zero; in combination with the brake B2, the rotating speed of the four-row planet carrier CA4 and the three-row gear ring R3 is zero; the second-row sun gear S2 and the output member II have the same rotating speed by combining the clutch C1;
the power is input through an input shaft I and transmitted to a three-row planet carrier CA3, is externally engaged with a three-row sun gear S3 through a three-row planet gear, is transmitted to a four-row gear ring R4 through a transmission member III, is transmitted to a one-row planet carrier CA1 and a two-row gear ring R2 through a transmission member V, is internally engaged with a one-row planet gear through a one-row gear ring R1 and is transmitted to a two-row planet carrier CA2 through a transmission member IV, is externally engaged with a two-row sun gear S2 through a two-row planet gear, and is output to an output member through a two-row sun gear S2 to realize R1 gear;
(9) the R2 gear is realized by combining the brake B1, the brake B2 and the clutch C3:
in combination with the brake B1, the rotating speed of the sun gear S1 in one row is zero; in combination with the brake B2, the rotating speed of the four-row planet carrier CA4 and the three-row gear ring R3 is zero; the combination of the clutch C3, a row of gear rings R1, a double-row planet carrier CA2 and a transmission member II have the same rotating speed;
the power is input and transmitted to a three-row planet carrier CA3 through an input shaft I, is externally engaged with a three-row sun gear S3 through three rows of planet gears, is transmitted to a four-row gear ring R4 through a transmission component III and four rows of engagement, is transmitted to a row of planet carrier CA1 and a two-row gear ring R2 through a transmission component V, and is internally engaged with a row of planet gears through a row of gear ring R1 and is transmitted to a row of gear ring R1 and an output component II to realize R2 gear;
(10) the R3 gear is realized by combining the brake B2, the clutch C1 and the clutch C3:
in combination with the brake B2, the rotating speed of the four-row planet carrier CA4 and the three-row gear ring R3 is zero; the second-row sun gear S2 and the transmission member II have the same rotating speed by combining the clutch C1; the combination of the clutch C3, a row of gear rings R1, a double-row planet carrier CA2 and a transmission member II have the same rotating speed;
the power is input and transmitted to a three-row planet carrier CA3 through an input shaft I, is externally engaged with a three-row sun gear S3 through three rows of planet gears, is transmitted to a four-row gear ring R4 through a transmission member III and four rows of engagement, is transmitted to a row of planet carrier CA1 and a two-row gear ring R2 through a transmission member V, and is transmitted to a row of gear ring R1 and an output member II through the inner engagement of a row of gear ring R1 and a row of planet gears, so that the R3 gear is realized.
CN202110306538.5A 2021-03-23 2021-03-23 Four-freedom-degree multi-gear planetary speed change mechanism for tracked vehicle Pending CN113074223A (en)

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Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CN202110306538.5A CN113074223A (en) 2021-03-23 2021-03-23 Four-freedom-degree multi-gear planetary speed change mechanism for tracked vehicle

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CN113074223A true CN113074223A (en) 2021-07-06

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Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103016653A (en) * 2011-09-21 2013-04-03 现代自动车株式会社 Transmission for vehicle
KR20130032962A (en) * 2011-09-26 2013-04-03 현대자동차주식회사 Transmission for vehicle
CN104246293A (en) * 2012-04-25 2014-12-24 Zf腓德烈斯哈芬股份公司 Multi-speed gearbox
CN104595436A (en) * 2015-02-13 2015-05-06 中国北方车辆研究所 Seven-gear planetary transmission for automatic transmission case

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103016653A (en) * 2011-09-21 2013-04-03 现代自动车株式会社 Transmission for vehicle
KR20130032962A (en) * 2011-09-26 2013-04-03 현대자동차주식회사 Transmission for vehicle
CN104246293A (en) * 2012-04-25 2014-12-24 Zf腓德烈斯哈芬股份公司 Multi-speed gearbox
CN104595436A (en) * 2015-02-13 2015-05-06 中国北方车辆研究所 Seven-gear planetary transmission for automatic transmission case

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