CN109630626B - Eight-front eight-reverse planetary speed change mechanism - Google Patents

Eight-front eight-reverse planetary speed change mechanism Download PDF

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Publication number
CN109630626B
CN109630626B CN201811445849.4A CN201811445849A CN109630626B CN 109630626 B CN109630626 B CN 109630626B CN 201811445849 A CN201811445849 A CN 201811445849A CN 109630626 B CN109630626 B CN 109630626B
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clutch
brake
gear
planet
planetary
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CN109630626A (en
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唐沛
邢庆坤
张鹤
张静
孙晨辉
李慎龙
李晋
高子茵
尹华兵
周如意
李新毅
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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
    • 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
    • F16H57/02—Gearboxes; Mounting gearing therein
    • F16H57/023—Mounting or installation of gears or shafts in the gearboxes, e.g. methods or means for assembly
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/02—Gearboxes; Mounting gearing therein
    • F16H2057/02039—Gearboxes for particular applications
    • F16H2057/02043—Gearboxes for particular applications for vehicle transmissions
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/02—Gearboxes; Mounting gearing therein
    • F16H2057/02086—Measures for reducing size of gearbox, e.g. for creating a more compact transmission casing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/02—Gearboxes; Mounting gearing therein
    • F16H2057/02091—Measures for reducing weight of gearbox
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/02—Gearboxes; Mounting gearing therein
    • F16H2057/02095—Measures for reducing number of parts or components
    • 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
    • F16H2200/006—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising eight 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
    • 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
    • F16H2200/2015—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with five 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
    • F16H2200/2051—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with eight 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 an eight-forward eight-reverse planetary speed change mechanism which can realize sixteen gears in total, and has the characteristics of high integration, high compactness, multiple gears, easiness in assembly and disassembly and the like. The planetary transmission includes: the double-ring meshing planetary gear train comprises two double-ring meshing planetary rows, two common planetary rows, eight control pieces and six transmission members, wherein the two double-ring meshing planetary rows are a first double-ring meshing planetary row and a second double-ring meshing planetary row respectively; the two common planet rows are a common negative planet row and a common positive planet row respectively; the eight operating parts are four clutches and four brakes respectively. The invention can realize sixteen gears with eight forward eight reverse directions by four planetary rows, the planetary transmission comprises two double internal meshing planetary rows and two common planetary rows, eight operating parts (four clutches and four brakes) are used for directly or indirectly connecting basic components of each row with an input shaft and an output shaft, and each gear is realized by reducing the rotational freedom degree of each basic component.

Description

Eight-front eight-reverse planetary speed change mechanism
Technical Field
The invention relates to a speed change mechanism, in particular to an eight-gear speed change mechanism for an automatic gearbox, and belongs to the field of design of speed change mechanisms.
Background
The speed change mechanism of the automatic gearbox adapts to the driving requirement of the vehicle by changing the rotating speed and the torque output by the hydraulic torque converter, the more gears of the automatic gearbox are, the more easily the transmission ratio series are optimized, and the better the dynamic property and the fuel economy of the whole vehicle are, so the scheme of realizing more gears is used as much as possible; the transmission efficiency, geometry and reliability of a planetary transmission depend to a large extent on the transmission diagram, which is preferably a complex and cumbersome operation. Therefore, it is necessary to provide a new compact and efficient transmission mechanism to improve the power performance and economy of the whole vehicle.
Disclosure of Invention
In view of this, the invention provides an eight-forward eight-reverse planetary transmission mechanism, which can realize sixteen gears in total, and has the characteristics of high integration, high compactness, multiple gears, easy assembly and disassembly, and the like.
The eight-front eight-reverse planetary speed change mechanism comprises: the transmission comprises a first double inner meshing planetary row, a first clutch, a first brake, a forward and reverse mechanism and a fourth-gear planetary speed change mechanism; the fourth-gear planetary speed change mechanism comprises a negative planetary row, a positive planetary row, a third clutch, a fourth clutch, a third brake and a fourth brake;
the first dual inner intermeshing planet row comprises: the planetary gear set comprises a first gear ring, a first planet carrier, a first sun gear and a first planet gear, wherein the first planet gear is provided with inner teeth and outer teeth, the outer teeth of the first planet gear are meshed with the first gear ring, the inner teeth of the first planet gear are meshed with the first sun gear, and the first planet carrier is used for supporting the first planet gear;
the minus planetary row includes: a third ring gear, a third planet carrier, a third sun gear and a third planet gear; the third planet gear is supported on the third planet carrier, and is internally meshed with the third gear ring and simultaneously externally meshed with the third sun gear; the positive planet row comprises a duplex planet wheel, a fourth sun wheel and a fifth sun wheel, and the positive planet row and the negative planet row share a third planet carrier, namely the duplex planet wheel is supported on the third planet carrier; the duplex planet wheel is respectively meshed with the fourth sun wheel and the fifth sun wheel;
the connection relationship is as follows: the input shaft is connected with a first double-inner-meshing planetary row, the first double-inner-meshing planetary row is connected with the fourth-gear planetary speed change mechanism through the forward and backward mechanism, and the method specifically comprises the following steps: the input shaft is connected with a first sun gear of the first double-inner meshing planetary row, the first planet carrier is respectively connected with an outer hub of the first clutch and an inner hub of the first brake, and the outer hub of the first brake is fixed; the first gear ring and the inner hub of the first clutch are respectively connected with the input end of the forward and backward mechanism; the output end of the forward-reverse mechanism is respectively connected with the fourth sun gear and the inner hub of the third clutch; the third sun gear is respectively connected with an outer hub of the third clutch and an inner hub of the third brake, and the outer hub of the third brake is fixed; the third gear ring is respectively connected with an outer hub of the fourth clutch and an inner hub of a fourth brake, and the outer hub of the fourth brake is fixed; the output shaft is connected with the fifth sun gear and the inner hub of the fourth clutch respectively.
The mechanism of just falling includes: a second dual intermeshing planet row, a second clutch and a second brake;
the double inner meshing planetary row includes: the second planet carrier, the second gear ring, the second sun gear and the second planet gear with inner and outer teeth; the outer teeth of the second planet wheel are meshed with a second gear ring, the inner teeth of the second planet wheel are meshed with a second sun wheel, and the second planet carrier is used for supporting the second planet wheel;
the second planet carrier serving as the input end of the forward and backward mechanism is respectively connected with the first gear ring and the inner hub of the first clutch, and the second sun gear serving as the output end of the forward and backward mechanism is respectively connected with the fourth sun gear and the inner hub of the third clutch;
the second clutch and the second brake are linked, namely when the second brake is combined, the second clutch is separated; when the second clutch is combined, the second brake is separated; when the second brake is combined, the second gear ring is braked; when the second clutch is combined, the second planet carrier and the second gear ring rotate synchronously.
The speed change mechanism is provided with eight forward gears which are respectively D1 gear to D8 gear:
when the first brake, the second clutch, the third brake and the fourth brake are combined, the gear D1 is achieved;
when the first clutch, the second clutch, the third brake and the fourth brake are combined, the gear D2 is achieved;
when the first brake, the second clutch, the third clutch and the fourth brake are combined, the gear D3 is achieved;
when the first clutch, the second clutch, the third clutch and the fourth brake are combined, the gear D4 is achieved;
when the first brake, the second clutch, the third brake and the fourth clutch are combined, the gear D5 is achieved;
when the first clutch, the second clutch, the third brake and the fourth clutch are combined, the gear D6 is achieved;
when the first brake, the second clutch, the third clutch and the fourth clutch are combined, the gear D7 is achieved;
and D8 gear when the first clutch, the second clutch, the third clutch and the fourth clutch are combined.
The speed change mechanism has eight reverse gears which are respectively R1 gears to R8 gears:
when the first brake, the second brake, the third brake and the fourth brake are combined, the gear R1 is
When the first clutch, the second brake, the third brake and the fourth brake are combined, the gear is R2;
when the first brake, the second brake, the third clutch and the fourth brake are combined, the gear R3 is achieved;
when the first clutch, the second brake, the third clutch and the fourth brake are combined, the gear R4 is achieved;
when the first brake, the second brake, the third brake and the fourth clutch are combined, the gear R5 is achieved;
when the first clutch, the second brake, the third brake and the fourth clutch are combined, the gear is R6;
when the first brake, the second brake, the third clutch and the fourth clutch are combined, the gear R7 is achieved;
when the first clutch, the second brake, the third clutch and the fourth clutch are combined, the gear R8 is achieved.
Has the advantages that:
(1) the eight-front eight-reverse planetary speed change mechanism adopts the double inner meshing planetary rows, the clutch C1 is linked with the brake B1, and the clutch C2 is linked with the brake B2, so that the number of parts and the size of an automatic gearbox are reduced, the weight of the gearbox is lightened, and the manufacturing cost is reduced.
(2) The invention can realize sixteen gears with eight forward eight reverse directions by four planetary rows, the planetary transmission is composed of two double internal meshing planetary rows and two common planetary rows, basic components (a gear ring, a planet carrier and a sun gear) of each row are directly or indirectly connected with an input shaft and an output shaft (or a box body) by eight operating parts (four clutches and four brakes), and each gear is realized by reducing the rotational freedom degree of each basic component.
Drawings
FIG. 1 is a diagrammatic view of the drive of the present invention;
wherein: 1-input shaft, 2-output shaft, 3-first transmission component, 4-second transmission component, 5-third transmission component, 6-fourth transmission component, 7-fifth transmission component and 8-sixth transmission component
Detailed Description
The present invention will be described in further detail with reference to the accompanying drawings and examples.
The embodiment provides an eight-front eight-reverse planetary speed change mechanism, which adopts double inner meshing planetary rows, optimizes a transmission diagram, can greatly reduce the whole size, improves the transmission efficiency and increases the transmission power.
The planetary speed change mechanism is suitable for a vehicle automatic transmission taking an engine or a motor as a power source, all planetary rows are arranged in sequence, the planetary rows are connected by a transmission member, an input shaft is connected with an input member, and the power output by the power source is transmitted to the planetary speed change mechanism; the output shaft is connected with the output member, and power is transmitted to the front and rear axles or the left and right driving wheels through a transfer case or a differential.
Specifically, as shown in fig. 1, the planetary transmission includes: the double-ring-meshing planetary gear train comprises two double ring-meshing planetary rows, two common planetary rows, eight control pieces and six transmission members, wherein the two double ring-meshing planetary rows are a first double ring-meshing planetary row CRG1 and a second double ring-meshing planetary row CRG2 respectively; the two common planet rows are a common negative planet row PGS1 and a common positive planet row PGS2 respectively; the eight operating pieces are a first clutch C1, a second clutch C2, a third clutch C3 and a fourth clutch C4 respectively; a first brake B1, a second brake B2, a third brake B3 and a fourth brake B4; the six transmission members are a first transmission member 3, a second transmission member 4, a third transmission member 5, a fourth transmission member 6, a fifth transmission member 7 and a sixth transmission member 8, respectively. The planetary transmission mechanism can realize eight forward gears, wherein the second double internal meshing planetary row CRG2 is a reversing row, when the speed ratio of the row is negative, eight reverse gears can be realized, if the vehicle is provided with other types of forward and reverse mechanisms, the row can be cancelled, and the rest of connection modes are unchanged. The first clutch C1 is linked with the first brake B1, namely when the first clutch C1 is combined, the first brake B1 is separated, and when the first clutch C1 is separated, the first brake B1 brakes; when the second clutch C2 and the second brake B2 are linked, that is, when the second clutch C2 is engaged, the second brake B2 is disengaged, and when the second clutch C2 is disengaged, the second brake B2 is braked.
The first double inner meshing planetary row CRG1 is composed of a first ring gear R1, a first carrier CA1, a first sun gear S1, and a first planetary gear having internal teeth and external teeth, the external teeth of which are engaged with the first ring gear R1, the internal teeth of which are engaged with the first sun gear S1, and the first carrier CA1 for supporting the first planetary gear. The second double inner meshing planetary line CRG2 is constituted and connected in the same manner as the first double inner meshing planetary line CRG1, and is constituted by a second ring gear R2, a second carrier CA2, a second sun gear S2, and a first planetary gear. Wherein the second planet wheel has an inner toothing and an outer toothing, the outer toothing of which meshes with the second ring gear R2, the inner toothing of which meshes with the second sun wheel S2, and a second planet carrier CA2 for supporting the second planet wheel.
Negative row PGS1 is made up of a third ring gear R3, a third carrier CA3, a third sun gear S3, each of which meshes with third ring gear R3 and also with third sun gear S3, and a number of third planets (typically 3 or 4) supported by third carrier CA 3. The plus planetary row PGS2 and the minus planetary row PGS1 share a third planet carrier CA3, and in addition, the plus planetary row PGS2 further includes a plurality of duplex planet wheels, a fourth sun wheel S4 and a fifth sun wheel S5, wherein each of the duplex planet wheels is respectively meshed with the fourth sun wheel S4 and the fifth sun wheel S5, and the third planet carrier CA3 supports the duplex planet wheels.
For two inter-meshing planetary rows CRG1 and CRG2, characteristic parameter k is the product of the number of teeth of the ring gear of the planetary row and the number of teeth of the internal tooth of the planetary wheel, the ratio of the product of the number of teeth of the external tooth of the planetary wheel and the number of teeth of the sun gear, both, for negative planetary row PGS1, characteristic parameter k is the ratio of the number of teeth of the third ring gear R3 and the number of teeth of the third sun gear S3, for positive planetary row PGS2, characteristic parameter k is the ratio between the product of the number of teeth of the fifth sun gear S5 and the meshing planetary gear thereof and the product of the number of teeth of the fourth sun gear S4 and the meshing planetary gear thereof, and the characteristic parameters of four planetary: k is a radical of1＝1.3687、k2＝1.4、k3＝3.1573、k43.2813, wherein k1Is a characteristic parameter, k, of the first double intermeshing row CRG12Is a characteristic parameter, k, of the second double intermeshing row CRG13Characteristic parameter, k, of minus planetary row PGS14Characteristic parameters of the plus planet row PGS 2.
The connection relationship is as follows: the input shaft 1 is connected to the first sun gear S1 of the first double inter-meshing planetary row CRG1, the first transmission member 3 is connected to the first carrier CA1, the outer hub of the first clutch C1 and the inner hub of the first brake B1, respectively, and the outer hub of the first brake B1 is fixed; the second transmission member 4 is connected to the first ring gear R1, the inner hub of the first clutch C1 and the second carrier CA2 of the second double internally meshing planetary row CRG2, respectively; the third transmission member 5 is respectively connected with the second ring gear R2 of the second double internally meshing planetary row CRG2, the outer hub of the second clutch C2 and the inner hub of the second brake B2, and the outer hub of the second brake B2 is fixed; the fourth transmission member 6 is connected to the inner hubs of the second sun gear S2 of the second double internally meshing planetary row CRG2, the fourth sun gear S4 of the plus planetary row PGS2 and the third clutch C3, respectively; the fifth transmission member 7 is connected with the third sun gear S3 of the negative planetary row PGS1, the outer hub of the third clutch C3 and the inner hub of the third brake B3, respectively, and the outer hub of the third brake B3 is fixed; the sixth transmission member 8 is connected to the third ring gear R3 of the minus planetary row PGS1, the outer hub of the fourth clutch C4 and the inner hub of the fourth brake B4, respectively, and the outer hub of the fourth brake B4 is fixed. The output shaft 2 is connected to the inner hubs of the fifth sun gear S5 and the fourth clutch C4, respectively. It follows that the first brake B1 is used to brake the first transmission member 3; a second brake B2 for braking the third transmission member 5, a third brake B3 for braking the fifth transmission member 7, a fourth brake B4 for braking the sixth transmission member 8; the first clutch C1 is used to connect the first transmission member 3 and the second transmission member 4; the second clutch C2 is used to connect the second transmission member 4 and the third transmission member 5; the third clutch C3 is used to connect the fourth transmission member 6 and the fifth transmission member 7; the fourth clutch C4 is used to connect the sixth transmission member 8 with the output shaft 2.
The following is a description of the implementation of each gear, and the eight forward gears implemented by the transmission mechanism are respectively marked as follows: d1, D2, D3, D4, D5, D6, D7, and D8, eight reverse gears implemented are labeled R1, R2, R3, R4, R5, R6, R7, and R8, respectively: because this derailleur is five degree of freedom derailleurs, realize that a certain gear needs four control pieces of action, eliminate another four degrees of freedom, can realize fixed input and output, now analyze as follows:
(1) the D1 gear is realized by combining the first brake B1, the second clutch C2, the third brake B3 and the fourth brake B4:
in conjunction with first brake B1, the first carrier CA1 of first double inter-meshing planetary row CRG1 has zero rotational speed, in conjunction with second clutch C2, the second carrier CA2 of second double inter-meshing planetary row CRG1 has the same rotational speed as that of second ring gear R2 (i.e., rotates in synchronization), in conjunction with third brake B3, the rotational speed of third sun gear S3 is zero, and in conjunction with fourth brake B4, the rotational speed of third ring gear R3 is zero.
At this time, power is input through the input shaft 1, since the rotation speed of the first carrier CA1 is zero, the power is input through the first sun gear S1, then is output to the second transmission member 4 after being reduced in speed by the first ring gear R1, since the rotation speed of the second carrier CA2 is the same as that of the second ring gear R2, the power is input through the second transmission member 4, then is output to the fourth transmission member 6 without variation through the second sun gear S2, since the rotation speeds of the third sun gear S3 and the third ring gear R3 are zero, the power is input through the fourth transmission member 6, then is output to the output shaft 2 through the fourth sun gear S4 and reduction in speed by the fifth sun gear S5, and thus the D1 gear is realized.
(2) The D2 gear is realized by combining the first clutch C1, the second clutch C2, the third brake B3 and the fourth brake B4:
when the first clutch C1 is engaged, the rotational speed of the first carrier CA1 is the same as that of the first ring gear R1, when the second clutch C2 is engaged, the rotational speed of the second carrier CA2 is the same as that of the second ring gear R2, when the third brake B3 is engaged, the rotational speed of the third sun gear S3 is zero, and when the fourth brake B4 is engaged, the rotational speed of the third ring gear R3 is zero.
At this time, power is input through the input shaft 1, since the first carrier CA1 has the same rotation speed as the first ring gear R1, the power is input through the first sun gear S1, and then is output to the second transmission member 4 through the first ring gear R1 without change, since the second carrier CA2 has the same rotation speed as the second ring gear R2, the power is input through the second transmission member 4, and then is output to the fourth transmission member 6 through the second sun gear S2 without change, since the rotation speeds of the third sun gear S3 and the third ring gear R3 are zero, the power is input through the fourth transmission member 6, and then is output to the output shaft 2 through the fifth sun gear S5 with a reduced speed through the fourth sun gear S4, thereby realizing the D2 stage.
(3) The D3 gear is realized by combining the first brake B1, the second clutch C2, the third clutch C3 and the fourth brake B4:
when first brake B1 is engaged, the rotational speed of first carrier CA1 is zero, second clutch C2 is engaged, the rotational speeds of second carrier CA2 and second ring gear R2 are the same, third clutch C3 is engaged, third sun gear S3 is the same as the rotational speeds of second sun gear S2 and fourth sun gear S4, brake B4 is engaged, and the rotational speed of third ring gear R3 is zero.
At this time, power is input through the input shaft 1, since the rotation speed of the first carrier CA1 is zero, the power is input through the first sun gear S1, is reduced in speed through the first ring gear R1, and is output to the second transmission member 4, since the rotation speed of the second carrier CA2 is the same as that of the second ring gear R2, the power is input through the second transmission member 4, is output to the fourth transmission member 6 without variation through the second sun gear S2, since the rotation speed of the third sun gear S3 is the same as that of the second sun gear S2, the rotation speed of the third ring gear R3 is zero, and after the power is input through the fourth transmission member 6, the power is reduced in speed through the fourth sun gear S4, and is output to the output shaft 2 through the fifth sun gear S5, thereby realizing the D3 gear.
(4) The D4 gear is realized by combining the first clutch C1, the second clutch C2, the third clutch C3 and the fourth brake B4:
when the first clutch C1 is engaged, the rotational speed of the first carrier CA1 is the same as that of the first ring gear R1, when the second clutch C2 is engaged, the rotational speed of the second carrier CA2 is the same as that of the second ring gear R2, when the third clutch C3 is engaged, the rotational speed of the third sun gear S3 is the same as that of the fourth sun gear S4, when the fourth brake B4 is engaged, the rotational speed of the third ring gear R3 is zero.
At this time, power is input through the input shaft 1, since the first carrier CA1 and the first ring gear R1 have the same rotation speed, the power is input through the first sun gear S1 and then output to the second transmission member 4 through the first ring gear R1 without change, since the second carrier CA2 and the second ring gear R2 have the same rotation speed, the power is input through the second transmission member 4 and then output to the fourth transmission member 6 through the second sun gear S2 without change, since the third sun gear S3 and the second row sun gear S2 are the same, the rotation speed of the third ring gear R3 is zero, and after the power is input through the fourth transmission member 6, the power is output to the output shaft 2 through the fourth sun gear S4 and the fifth sun gear S5 with a reduction, thereby realizing the D4 gear.
(5) The D5 gear is realized by combining the first brake B1, the second clutch C2, the third brake B3 and the fourth clutch C4:
with the first brake B1, the rotational speed of the first carrier CA1 is zero, with the second clutch C2, the rotational speed of the second carrier CA2 is the same as that of the second ring gear R2, with the third brake B3, the rotational speed of the third sun gear S3 is zero, with the fourth clutch C4, the rotational speed of the third ring gear R3 is the same as that of the fifth sun gear S5.
At this time, power is input through the input shaft 1, the rotational speed of the first carrier CA1 is zero, the power is input through the first sun gear S1, then the power is output to the second transmission member 4 with a reduced speed through the first ring gear R1, the rotational speed of the second carrier CA2 is the same as that of the second ring gear R2, the power is input through the second transmission member 4, then the power is output to the fourth transmission member 6 without variation through the second sun gear S2, the rotational speed of the third sun gear S3 is zero, the rotational speed of the third ring gear R3 is the same as that of the fifth sun gear S5, the power is input through the fourth transmission member 6, then the power is output to the output shaft 2 with a reduced speed through the fourth sun gear S4 and the fifth sun gear S5, and thus the D5 gear is realized.
(6) The D6 gear is realized by combining the first clutch C1, the second clutch C2, the third brake B3 and the fourth clutch C4:
when the first clutch C1 is engaged, the rotational speed of the first carrier CA1 is the same as that of the first ring gear R1, when the second clutch C2 is engaged, the rotational speed of the second carrier CA2 is the same as that of the second ring gear R2, when the third brake B3 is engaged, the rotational speed of the third sun gear S3 is zero, and when the fourth clutch C4 is engaged, the rotational speed of the third ring gear R3 is the same as that of the fifth sun gear S5.
At this time, power is input through the input shaft 1, the first carrier CA1 and the first ring gear R1 have the same rotation speed, the power is input through the first sun gear S1 and then output to the second transmission member 4 through the first ring gear R1 without change, the power is input through the second transmission member 4 and then output to the fourth transmission member 6 through the second sun gear S2 without change because the second carrier CA2 and the second ring gear R2 have the same rotation speed, the third ring gear R3 and the fifth sun gear S5 have the same rotation speed because the rotation speed of the third sun gear S3 is zero, and the power is input through the fourth transmission member 6 and then output to the output shaft 2 through the fourth sun gear S4 and the fifth sun gear S5 with reduced speed, thereby realizing the D5 gear.
(7) The D7 gear is realized by combining the first brake B1, the second clutch C2, the third clutch C3 and the fourth clutch C4:
when first brake B1 is engaged, the rotational speed of first carrier CA1 is zero, second clutch C2 is engaged, the rotational speeds of second carrier CA2 and second ring gear R2 are the same, third clutch C3 is engaged, third sun gear S3 and fourth sun gear S4 are the same, fourth clutch C4 is engaged, and third ring gear R3 and fifth sun gear S5 are the same.
At this time, power is input through the input shaft 1, and since the rotation speed of the first carrier CA1 is zero, the power is input through the first sun gear S1, then output to the second transmission member 4 with a reduced speed through the first ring gear R1, since the rotation speed of the second carrier CA2 is the same as that of the second ring gear R2, the power is input through the second transmission member 4, then output to the fourth transmission member 6 without variation through the second sun gear S2, since the rotation speed of the third sun gear S3 is the same as that of the second sun gear S2, the rotation speed of the third ring gear R3 is the same as that of the fifth sun gear S5, and after the power is input through the fourth transmission member 6, the power is output to the output shaft 2 without variation through the fourth sun gear S4 and the fifth sun gear S5, thereby achieving the D7 gear.
(8) The D8 gear is realized by combining the first clutch C1, the second clutch C2, the third clutch C3 and the fourth clutch C4:
when the first clutch C1 is engaged, the first carrier CA1C has the same rotational speed as the first ring gear R1, when the second clutch C2 is engaged, the second carrier CA2 has the same rotational speed as the second ring gear R2, when the third clutch C3 is engaged, the third sun gear S3 has the same rotational speed as the fourth sun gear S4, when the fifth clutch C4 is engaged, the third ring gear R3 has the same rotational speed as the fifth sun gear S5.
At this time, power is input through the input shaft 1, the first carrier CA1 and the first ring gear R1 rotate at the same speed, the power is input through the first sun gear S1 and then output to the second transmission member 4 through the first ring gear R1 without change, the power is input through the second transmission member 4 and then output to the fourth transmission member 6 through the second sun gear S2 without change because the second carrier CA2 and the second ring gear R2 rotate at the same speed, the power is input through the fourth transmission member 6 and then output to the output shaft 2 through the fourth sun gear S4 and the fifth sun gear S5 without change because the third sun gear S3 and the second sun gear S2 rotate at the same speed, and thus the D8 gear is realized.
(9) When the reverse gear is performed, the second brake B2 is always in a combined state, and the rotating speed of the second ring gear R2 is zero;
the R1 gear is realized by combining a first brake B1, a second brake B2, a third brake B3 and a fourth brake B4;
in conjunction with first brake B1, the first carrier CA1 of first double inter-meshing planetary row CRG1 has zero rotational speed, in conjunction with second brake B2, the second ring gear R2 has zero rotational speed, in conjunction with third brake B3, the third sun gear S3 has zero rotational speed, and in conjunction with fourth brake B4, the third ring gear R3 has zero rotational speed.
At this time, power is input through the input shaft 1, since the rotation speed of the first carrier CA1 is zero, the power is input through the first sun gear S1, is output to the second transmission member 4 after being reduced through the first ring gear R1, the rotation speed of the second ring gear R2 is zero,
since the second carrier CA2 has the same rotational speed as the second ring gear R2, power is input through the second transmission member 4, and then output to the fourth transmission member 6 without change through the second sun gear S2, and since the rotational speeds of the third sun gear S3 and the third ring gear R3 are zero, power is input through the fourth transmission member 6, and then output to the output shaft 2 through the fourth sun gear S4 and the fifth sun gear S5 with a reduced speed, thereby implementing the R1 gear.
The R2 gear is realized by combining the first clutch C1, the second brake B2, the third brake B3 and the fourth brake B4;
the R3 gear is realized by combining the first brake B1, the second brake B2, the third clutch C3 and the fourth brake B4;
the R4 gear is realized by combining the first clutch C1, the second brake B2, the third clutch C3 and the fourth brake B4;
the R5 gear is realized by combining the first brake B1, the second brake B2, the third brake B3 and the fourth clutch C4;
the R6 gear is realized by combining the first clutch C1, the second brake B2, the third brake B3 and the fourth clutch C4;
the R7 gear is realized by combining the first brake B1, the second brake B2, the third clutch C3 and the fourth clutch C4;
the R8 speed is achieved in combination with the first clutch C1, the second brake B2, the third clutch C3 and the fourth clutch C4.
Table 1 shows the planetary transmission gears and ratios, which describes the operating members that need to be engaged to achieve each gear, while giving the step ratios between the gears.
TABLE 1 operating member combination sequence and transmission ratio for realizing each gear
Figure GDA0002423100900000081
Figure GDA0002423100900000091
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 (4)

1. An eight-front eight-reverse planetary speed change mechanism, comprising: the transmission comprises a first double inner meshing planetary row, a first clutch, a first brake, a forward and reverse mechanism and a fourth-gear planetary speed change mechanism; the fourth-gear planetary speed change mechanism comprises a negative planetary row, a positive planetary row, a third clutch, a fourth clutch, a third brake and a fourth brake;
the first dual inner intermeshing planet row comprises: the planetary gear set comprises a first gear ring, a first planet carrier, a first sun gear and a first planet gear, wherein the first planet gear is provided with inner teeth and outer teeth, the outer teeth of the first planet gear are meshed with the first gear ring, the inner teeth of the first planet gear are meshed with the first sun gear, and the first planet carrier is used for supporting the first planet gear;
the minus planetary row includes: a third ring gear, a third planet carrier, a third sun gear and a third planet gear; the third planet gear is supported on the third planet carrier, and is internally meshed with the third gear ring and simultaneously externally meshed with the third sun gear; the positive planet row comprises a duplex planet wheel, a fourth sun wheel and a fifth sun wheel, and the positive planet row and the negative planet row share a third planet carrier, namely the duplex planet wheel is supported on the third planet carrier; the duplex planet wheel is respectively meshed with the fourth sun wheel and the fifth sun wheel;
the connection relationship is as follows: the input shaft is connected with a first double-inner-meshing planetary row, the first double-inner-meshing planetary row is connected with the fourth-gear planetary speed change mechanism through the forward and backward mechanism, and the method specifically comprises the following steps: the input shaft is connected with a first sun gear of the first double-inner meshing planetary row, the first planet carrier is respectively connected with an outer hub of the first clutch and an inner hub of the first brake, and the outer hub of the first brake is fixed; the first gear ring and the inner hub of the first clutch are respectively connected with the input end of the forward and backward mechanism; the output end of the forward-reverse mechanism is respectively connected with the fourth sun gear and the inner hub of the third clutch; the third sun gear is respectively connected with an outer hub of the third clutch and an inner hub of the third brake, and the outer hub of the third brake is fixed; the third gear ring is respectively connected with an outer hub of the fourth clutch and an inner hub of a fourth brake, and the outer hub of the fourth brake is fixed; the output shaft is connected with the fifth sun gear and the inner hub of the fourth clutch respectively.
2. The eight-forward eight-reverse planetary transmission mechanism according to claim 1, wherein the forward-reverse mechanism comprises: a second dual intermeshing planet row, a second clutch and a second brake;
the second dual intermeshing planet row comprises: the second planet carrier, the second gear ring, the second sun gear and the second planet gear with inner and outer teeth; the outer teeth of the second planet wheel are meshed with a second gear ring, the inner teeth of the second planet wheel are meshed with a second sun wheel, and the second planet carrier is used for supporting the second planet wheel;
the second planet carrier serving as the input end of the forward and backward mechanism is respectively connected with the first gear ring and the inner hub of the first clutch, and the second sun gear serving as the output end of the forward and backward mechanism is respectively connected with the fourth sun gear and the inner hub of the third clutch;
the second clutch and the second brake are linked, namely when the second brake is combined, the second clutch is separated; when the second clutch is combined, the second brake is separated; when the second brake is combined, the second gear ring is braked; when the second clutch is combined, the second planet carrier and the second gear ring rotate synchronously.
3. The eight-forward eight-reverse planetary transmission as claimed in claim 2, wherein the transmission has eight forward gears, D1-D8:
when the first brake, the second clutch, the third brake and the fourth brake are combined, the gear D1 is achieved;
when the first clutch, the second clutch, the third brake and the fourth brake are combined, the gear D2 is achieved;
when the first brake, the second clutch, the third clutch and the fourth brake are combined, the gear D3 is achieved;
when the first clutch, the second clutch, the third clutch and the fourth brake are combined, the gear D4 is achieved;
when the first brake, the second clutch, the third brake and the fourth clutch are combined, the gear D5 is achieved;
when the first clutch, the second clutch, the third brake and the fourth clutch are combined, the gear D6 is achieved;
when the first brake, the second clutch, the third clutch and the fourth clutch are combined, the gear D7 is achieved;
and D8 gear when the first clutch, the second clutch, the third clutch and the fourth clutch are combined.
4. The eight-forward eight-reverse planetary transmission mechanism according to claim 2, wherein the transmission mechanism has eight reverse gears, R1-R8:
when the first brake, the second brake, the third brake and the fourth brake are combined, the gear R1 is
When the first clutch, the second brake, the third brake and the fourth brake are combined, the gear is R2;
when the first brake, the second brake, the third clutch and the fourth brake are combined, the gear R3 is achieved;
when the first clutch, the second brake, the third clutch and the fourth brake are combined, the gear R4 is achieved;
when the first brake, the second brake, the third brake and the fourth clutch are combined, the gear R5 is achieved;
when the first clutch, the second brake, the third brake and the fourth clutch are combined, the gear is R6;
when the first brake, the second brake, the third clutch and the fourth clutch are combined, the gear R7 is achieved;
when the first clutch, the second brake, the third clutch and the fourth clutch are combined, the gear R8 is achieved.
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CN113175506B (en) * 2021-04-20 2023-10-31 中国北方车辆研究所 Eight-gear compound planetary transmission mechanism with three degrees of freedom
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