CN111609098A - Modular design gearbox and gear implementation method - Google Patents

Modular design gearbox and gear implementation method Download PDF

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Publication number
CN111609098A
CN111609098A CN202010405265.5A CN202010405265A CN111609098A CN 111609098 A CN111609098 A CN 111609098A CN 202010405265 A CN202010405265 A CN 202010405265A CN 111609098 A CN111609098 A CN 111609098A
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China
Prior art keywords
gear
rotates
fixed gear
floating
clutch
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CN202010405265.5A
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Chinese (zh)
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CN111609098B (en
Inventor
詹东安
石国国
吕昌
闫伟朋
张刚
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Jiangsu XCMG Construction Machinery Institute Co Ltd
Jiangsu Advanced Construction Machinery Innovation Center Ltd
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Jiangsu XCMG Construction Machinery Institute Co Ltd
Jiangsu Advanced Construction Machinery Innovation Center Ltd
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Priority to CN202010405265.5A priority Critical patent/CN111609098B/en
Publication of CN111609098A publication Critical patent/CN111609098A/en
Priority to JP2021536756A priority patent/JP7113470B2/en
Priority to PCT/CN2020/133743 priority patent/WO2021227455A1/en
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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
    • F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
    • F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
    • F16H3/087—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears
    • F16H3/093—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears with two or more countershafts
    • 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
    • F16H3/006—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion power being selectively transmitted by either one of the parallel flow paths
    • 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
    • F16H2200/0095—Transmissions for multiple ratios characterised by the number of reverse speeds the gear ratios comprising four 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
    • F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
    • F16H2200/2048—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with seven engaging means

Abstract

The invention relates to a modularly designed gearbox and a gear implementation method. The gearbox can realize the highest forward 8-gear and reverse 4-gear mode, meets the requirements of special machinery on 8 forward gears, can control different clutches to be combined and adjusted into forward 7-gear and reverse 3-gear modes, forward 6-gear and reverse 3-gear modes and the like, and meets the requirements of different hosts; in addition, under the condition of not changing a transmission route, the speed ratio of each gear of the gearbox can be flexibly adjusted; secondly, under the condition that a box body of the gearbox is not changed, part of parts are changed or deleted, and different speed ratios and gear requirements are met; the gearbox body is kept unchanged, the modular design of the gearbox is realized, the generalization rate of parts of the gearbox is improved, and the production cost of the gearbox is reduced.

Description

Modular design gearbox and gear implementation method
Technical Field
The invention relates to the technical field of gearboxes, in particular to a modularly designed gearbox and a gear implementation method.
Background
At present, the engineering mechanical gearbox can be divided into a coaxial type and a balance shaft type according to the arrangement mode of a transmission shaft. The coaxial gearbox is mainly characterized in that an input shaft and an output shaft of the gearbox are coaxial, and the coaxial gearbox is mainly applied to engineering vehicles with the axes of the output end of an engine and the input end of a drive axle in the same plane; the balance shaft type gearbox is mainly applied to engineering vehicles with certain shaft drop between the output shaft of an engine and the input end axis of a drive axle.
The coaxial gearbox mainly adopts a planetary gear structure to transmit power and switch gears, the gearbox with the structure is compact in structure, small in required space and complex in structure, in order to obtain more gears, the planetary gear structure is usually connected in series, the adjustment range of each gear ratio is relatively narrow, and the maintenance cost is high.
The balance shaft type gearbox mainly adopts a plurality of transmission shafts and a plurality of gear pair meshing structures to carry out power transmission and gear switching, shafting are arranged in a balance mode, and a certain shaft descending distance is reserved between an input shaft and an output shaft, so that the structure is large in required space, simple in transmission route, relatively wide in adjustment range of speed ratios of various gears, even the number of teeth of a pair of gear pairs is changed, transmission ratios in a large range can be obtained, and maintenance cost is low.
The balanced gearbox can be divided into two types according to the arrangement mode of the clutches on the shaft, wherein one type is that two clutch packs are arranged on the shaft, and the other type is that one clutch pack is arranged on the shaft. The prior technical scheme only has a forward 6 gear and a reverse 3 gear at most, and simultaneously can realize a forward 5 gear, a reverse 3 gear, a forward 4 gear, a reverse 3 gear, a forward 3 gear, a reverse 3 gear and the like by controlling the combination modes of different clutches.
The existing gearbox cannot meet the requirement of 8 forward gears, and for special machines such as a land leveler and the like, the 8 forward gears are needed to meet the requirements of different working conditions. In addition, the gear speed ratio adjusting range of the existing gearbox can only be realized within 0.6-6.
Disclosure of Invention
Aiming at the defects in the prior art, the invention provides the transmission with the modular design, which can realize 8 forward gears and 4 backward gears, can realize 4 forward gears and 4 backward gears by only reducing part of components under the condition of not changing the structure of a box body, realizes the modular design, has high generalization rate and reduces the production cost of the transmission.
As one aspect of the invention, a modular design transmission is provided.
The modularized design gearbox includes the box, still includes:
a drive shaft S1 on which a fixed gear Z1 and a fixed gear Z2 are provided;
an intermediate shaft S2 on which a fixed gear Z3 and a floating gear Z14 mounted by a clutch C1 are provided; the fixed gear Z3 meshes with the fixed gear Z1;
an intermediate shaft S4 on which a fixed gear Z4, a fixed gear Z5 and a floating gear Z15 mounted by a clutch C2 are provided; the floating gear Z15 is meshed with the fixed gear Z2;
an intermediate shaft S3 on which a fixed gear Z6 and a floating gear Z16 mounted by a clutch C3 are provided; the fixed gear Z6 is meshed with the fixed gear Z1, and the floating gear Z16 is meshed with the fixed gear Z5;
an intermediate shaft S5 on which a fixed gear Z7 and a floating gear Z17 mounted by a clutch C4 are provided; the fixed gear Z7 meshes with the floating gear Z14, and the fixed gear Z7 meshes with the fixed gear Z5;
an intermediate shaft S6 on which a fixed gear Z8 and a floating gear Z18 mounted by a clutch C5 are provided; the fixed gear Z8 is meshed with the fixed gear Z7, and the floating gear Z18 is meshed with the floating gear Z17;
an intermediate shaft S7 on which a fixed gear Z9, a fixed gear Z10 and a floating gear Z19 mounted by a clutch C6 are provided; the fixed gear Z9 meshes with the fixed gear Z4;
an intermediate shaft S8 on which is disposed fixed gear Z11 and a floating gear set mounted via clutch C7; the fixed gear Z11 meshes with the fixed gear Z10, and the floating gear set meshes with the floating gear Z19;
an output shaft S9 on which a fixed gear Z12 and a fixed gear Z13 are provided; the fixed gear Z12 is in mesh with the floating gear Z18, and the fixed gear Z13 is in mesh with the floating gear set;
in the forward mode, the drive shaft S1, the intermediate shaft S5, the intermediate shaft S7, and the output shaft S9 rotate in the same direction and in the opposite direction to the intermediate shaft S2, the intermediate shaft S4, the intermediate shaft S6, and the intermediate shaft S8;
in the reverse shift mode, the drive shaft S1, the intermediate shaft S4, the intermediate shaft S6, and the intermediate shaft S8 rotate in the same direction, and in the opposite direction to the rotation of the intermediate shaft S3, the intermediate shaft S5, the intermediate shaft S7, and the output shaft S9.
Optionally, the floating gear set comprises a floating gear Z20 and a floating gear Z21 which are coaxially and fixedly connected, the floating gear Z20 is meshed with the floating gear Z19, and the floating gear Z21 is meshed with the fixed gear Z13; alternatively, the floating gear set includes only floating gear Z22, the floating gear Z22 is in mesh with the floating gear Z19, and the floating gear Z22 is in mesh with the fixed gear Z13.
As another aspect of the invention, a gear implementation method for a modular design gearbox is provided.
A gear implementation method of the modular design gearbox as described above is used for implementing a multi-gear mode and a low-gear mode, wherein the multi-gear mode comprises a forward 8-gear/reverse 4-gear mode, and the low-gear mode comprises a forward 4-gear/reverse 4-gear mode;
when the clutch C6 is in the engaged state, a first output path is formed from the fixed gear Z4, through the fixed gear Z9, the floating gear Z19, the floating gear set, to the fixed gear Z13;
when the clutch C7 is in the engaged state, a second output path is formed from the fixed gear Z4, through the fixed gear Z9, the fixed gear Z10, the fixed gear Z11, the floating gear set, to the fixed gear Z13;
when the clutch C4 is in the engaged state, a third output path is formed from the fixed gear Z7, through floating gear Z17, the floating gear Z18, to the fixed gear Z12;
when the clutch C5 is in the engaged state, a fourth output path is formed from the fixed gear Z7, through the fixed gear Z8, the floating gear Z18, to the fixed gear Z12;
forward 8/reverse 4 mode wherein:
advancing to a 1 gear: the clutch C1 and the clutch C6 are engaged, and the driving shaft S1 rotates the fixed gear Z1, rotates the fixed gear Z3, rotates the floating gear Z14, rotates the fixed gear Z7, rotates the fixed gear Z5, and then transmits power to the output shaft S9 through the first output path;
advancing for 2 gears: the clutch C2 and the clutch C6 are engaged, and the driving shaft S1 rotates the fixed gear Z2, rotates the floating gear Z15, and transmits power to the output shaft S9 through the first output path;
advancing in a 3-gear: the clutch C1 and the clutch C7 are engaged, and the driving shaft S1 rotates the fixed gear Z1, rotates the fixed gear Z3, rotates the floating gear Z14, rotates the fixed gear Z7, rotates the fixed gear Z5, and then transmits power to the output shaft S9 through the second output path;
advancing for 4 gears: the clutch C2 and the clutch C7 are engaged, and the driving shaft S1 rotates the fixed gear Z2, rotates the floating gear Z15, and transmits power to the output shaft S9 through the second output path;
advancing in 5 gears: the clutch C1 and the clutch C4 are engaged, and the driving shaft S1 rotates the fixed gear Z1, rotates the fixed gear Z3, rotates the floating gear Z14, and then transmits power to the output shaft S9 via the third output path;
advancing for 6 gears: the clutch C2 and the clutch C4 are engaged, the driving shaft S1 rotates the fixed gear Z2, rotates the floating gear Z15, rotates the fixed gear Z5, and then transmits power to the output shaft S9 via the third output path;
advancing to 7 gears: the clutch C1 and the clutch C5 are engaged, and the driving shaft S1 rotates the fixed gear Z1, rotates the fixed gear Z3, rotates the floating gear Z14, and then transmits power to the output shaft S9 via the fourth output path;
advancing for 8 gears: the clutch C2 and the clutch C5 are engaged, the driving shaft S1 rotates the fixed gear Z2, rotates the floating gear Z15, rotates the fixed gear Z5, and then transmits power to the output shaft S9 via the fourth output path;
backing off a 1 gear: the clutch C3 and the clutch C6 are engaged, and the driving shaft S1 rotates the fixed gear Z1, rotates the fixed gear Z6, rotates the floating gear Z16, rotates the fixed gear Z5, and then transmits power to the output shaft S9 through the first output path;
backing off 2 gears: the clutch C3 and the clutch C7 are engaged, and the driving shaft S1 rotates the fixed gear Z1, rotates the fixed gear Z6, rotates the floating gear Z16, rotates the fixed gear Z5, and then transmits power to the output shaft S9 through the second output path;
backing off 3 gears: the clutch C3 and the clutch C4 are engaged, and the driving shaft S1 rotates the fixed gear Z1, rotates the fixed gear Z6, rotates the floating gear Z16, rotates the fixed gear Z5, and then transmits power to the output shaft S9 through the third output path;
4, backing off: the clutch C3 and the clutch C5 are engaged, and the driving shaft S1 rotates the fixed gear Z1, rotates the fixed gear Z6, rotates the floating gear Z16, rotates the fixed gear Z5, and then transmits power to the output shaft S9 through the fourth output path;
in forward 4/reverse 4 mode, none of the countershaft S2, the fixed gear Z3, the clutch C1, and the floating gear Z14 are engaged in drive, wherein:
advancing to a 1 gear: the transmission path is the same as that of the forward 2 gear in the forward 8-gear/reverse 4-gear mode;
advancing for 2 gears: the transmission path is the same as that of the forward 4 gear in the forward 8-gear/reverse 4-gear mode;
advancing in a 3-gear: the transmission path is the same as that of the forward 6 gear in the forward 8-gear/reverse 4-gear mode;
advancing for 4 gears: the transmission path is the same as that of the forward 8 gear in the forward 8-gear/reverse 4-gear mode;
backing off a 1 gear: the same as the transmission path of reverse 1 gear in the forward 8-gear/reverse 4-gear mode;
backing off 2 gears: the transmission path is the same as that of the reverse 2 gear in the forward 8-gear/reverse 4-gear mode;
backing off 3 gears: the same as the transmission path of reverse 3 gear in the forward 8-gear/reverse 4-gear mode;
4, backing off: the same as the reverse 4-speed transmission path in the forward 8-speed/reverse 4-speed mode.
Optionally, the floating gear set comprises a floating gear Z20 and a floating gear Z21 which are coaxially and fixedly connected, the floating gear Z20 is meshed with the floating gear Z19, and the floating gear Z21 is meshed with the fixed gear Z13; alternatively, the floating gear set includes only floating gear Z22, the floating gear Z22 is in mesh with the floating gear Z19, and the floating gear Z22 is in mesh with the fixed gear Z13.
Alternatively, the forward 4/reverse 4 mode can also be achieved by:
fixed gear Z23 is disposed on the countershaft S3, the fixed gear Z23 is meshed with the fixed gear Z2, none of the countershaft S2, the fixed gear Z1, the fixed gear Z3, the clutch C1, the floating gear Z14 and the fixed gear Z6 participate in transmission, wherein:
advancing to a 1 gear: the transmission path is the same as that of the forward 2 gear in the forward 8-gear/reverse 4-gear mode;
advancing for 2 gears: the transmission path is the same as that of the forward 4 gear in the forward 8-gear/reverse 4-gear mode;
advancing in a 3-gear: the transmission path is the same as that of the forward 6 gear in the forward 8-gear/reverse 4-gear mode;
advancing for 4 gears: the transmission path is the same as that of the forward 8 gear in the forward 8-gear/reverse 4-gear mode;
backing off a 1 gear: the clutch C3 and the clutch C6 are engaged, and the driving shaft S1 rotates the fixed gear Z2, rotates the fixed gear Z23, rotates the floating gear Z16, rotates the fixed gear Z5, and then transmits power to the output shaft S9 through the first output path;
backing off 2 gears: the clutch C3 and the clutch C7 are engaged, and the driving shaft S1 rotates the fixed gear Z2, rotates the fixed gear Z23, rotates the floating gear Z16, rotates the fixed gear Z5, and then transmits power to the output shaft S9 through the second output path;
backing off 3 gears: the clutch C3 and the clutch C4 are engaged, and the driving shaft S1 rotates the fixed gear Z2, rotates the fixed gear Z23, rotates the floating gear Z16, rotates the fixed gear Z5, and then transmits power to the output shaft S9 through the third output path;
4, backing off: the clutch C3 and the clutch C5 are engaged, and the driving shaft S1 rotates the fixed gear Z2, rotates the fixed gear Z23, rotates the floating gear Z16, rotates the fixed gear Z5, and then transmits power to the output shaft S9 through the fourth output path.
The technical scheme of the invention has the beneficial effects that: the invention provides a modularly designed gearbox and a gear implementation method, which can realize a highest forward 8-gear and reverse 4-gear mode, meet the requirements of special machinery on 8 forward gears, simultaneously control different clutches to be combined and further adjust the modes of forward 7-gear and reverse 3-gear, forward 6-gear and reverse 3-gear, forward 5-gear and reverse 3-gear and forward 4-gear and reverse 3-gear, and meet the requirements of different hosts on different gears; in addition, under the condition of not changing a transmission route, the speed ratio of each gear of the gearbox can be flexibly adjusted; secondly, under the condition that a box body of the gearbox is not changed, part of parts are changed or deleted, and different speed ratios and gear requirements are met; the gearbox body is kept unchanged, the modular design of the gearbox is realized, the generalization rate of parts of the gearbox is improved, and the production cost of the gearbox is reduced.
Drawings
FIG. 1 is a first schematic transmission diagram of the modular transmission of the present invention in forward 8-speed/reverse 4-speed mode;
FIG. 2 is a schematic axial end view of the structure of FIG. 1;
FIG. 3 is a second schematic diagram of the forward 8-speed/reverse 4-speed transmission mode of the modular gearbox of the present invention
FIG. 4 is a first transmission schematic in forward 4-speed/reverse 4-speed mode of the modular design transmission of the present invention;
FIG. 5 is a second transmission schematic in forward 4-speed/reverse 4-speed mode of the modular design transmission of the present invention.
Detailed Description
Exemplary embodiments of the present invention are described below with reference to the accompanying drawings, in which various details of embodiments of the invention are included to assist understanding, and which are to be considered as merely exemplary. Accordingly, those of ordinary skill in the art will recognize that various changes and modifications of the embodiments described herein can be made without departing from the scope and spirit of the invention. Also, descriptions of well-known functions and constructions are omitted in the following description for clarity and conciseness.
Referring to fig. 1 and 2, the modular gearbox of the present invention comprises a casing, and a driving shaft S1, intermediate shafts S2-S8 and an output shaft S9 arranged in the casing, wherein a fixed gear Z1 and a fixed gear Z2 are arranged on the driving shaft S1; a fixed gear Z3 and a floating gear Z14 mounted through a clutch C1 are arranged on the intermediate shaft S2; the fixed gear Z3 is meshed with the fixed gear Z1; the intermediate shaft S4 is provided with a fixed gear Z4, a fixed gear Z5 and a floating gear Z15 mounted through a clutch C2; the floating gear Z15 is meshed with the fixed gear Z2; a fixed gear Z6 and a floating gear Z16 mounted through a clutch C3 are arranged on the intermediate shaft S3; the fixed gear Z6 is meshed with the fixed gear Z1, and the floating gear Z16 is meshed with the fixed gear Z5; a fixed gear Z7 and a floating gear Z17 mounted through a clutch C4 are arranged on the intermediate shaft S5; the fixed gear Z7 is meshed with the floating gear Z14, and the fixed gear Z7 is meshed with the fixed gear Z5; a fixed gear Z8 and a floating gear Z18 mounted through a clutch C5 are arranged on the intermediate shaft S6; the fixed gear Z8 is meshed with the fixed gear Z7, and the floating gear Z18 is meshed with the floating gear Z17; the intermediate shaft S7 is provided with a fixed gear Z9, a fixed gear Z10 and a floating gear Z19 mounted through a clutch C6; the fixed gear Z9 is meshed with the fixed gear Z4; the intermediate shaft S8 is provided with a fixed gear Z11, a floating gear Z20 and a floating gear Z21 which are arranged through a clutch C7; the fixed gear Z11 is meshed with the fixed gear Z10, and the floating gear Z20 is meshed with the floating gear Z19; the output shaft S9 is provided with a fixed gear Z12 and a fixed gear Z13; fixed gear Z12 meshes with floating gear Z18, and fixed gear Z13 meshes with floating gear Z21.
In the forward gear mode, the rotation directions of the driving shaft S1, the intermediate shaft S5, the intermediate shaft S7 and the output shaft S9 are the same, and are opposite to the rotation directions of the intermediate shaft S2, the intermediate shaft S4, the intermediate shaft S6 and the intermediate shaft S8; in the reverse mode, the drive shaft S1, the intermediate shaft S4, the intermediate shaft S6, and the intermediate shaft S8 rotate in the same direction, but in the opposite direction to the rotation of the intermediate shafts S3, S5, S7, and S9.
As shown in fig. 3, as another embodiment of the present invention, it is different from the above-described embodiment in that the floating gear Z20 and the floating gear Z21 are replaced with a floating gear Z22, and the floating gear Z19 and the fixed gear Z13 are both engaged with a floating gear Z22.
The gear implementation method of the modular gearbox of the present invention is explained below.
The transmission of the above structure can realize a multi-gear mode including a forward 8-gear/reverse 4-gear mode and a low-gear mode including a forward 4-gear/reverse 4-gear mode.
When clutch C6 is in the engaged state, a first output path is formed from fixed gear Z4, through fixed gear Z9, floating gear Z19, the floating gear set, to fixed gear Z13; when clutch C7 is in the engaged state, a second output path is formed from fixed gear Z4, fixed gear Z9, fixed gear Z10, fixed gear Z11, the floating gear set to fixed gear Z13; when clutch C4 is in the engaged state, a third output path is formed from fixed gear Z7, through floating gear Z17, floating gear Z18, to fixed gear Z12; when clutch C5 is in the engaged state, a fourth output path is formed from fixed gear Z7, through fixed gear Z8, floating gear Z18, to fixed gear Z12;
as shown in fig. 4, in one embodiment, a forward 8/reverse 4 mode wherein:
advancing to a 1 gear: when the clutch C1 and the clutch C6 are in a combined state, the driving shaft S1 drives the fixed gear Z1 to rotate, drives the fixed gear Z3 to rotate, drives the floating gear Z14 to rotate, drives the fixed gear Z7 to rotate, drives the fixed gear Z5 to rotate, and then transmits power to the output shaft S9 through a first output path;
advancing for 2 gears: the clutch C2 and the clutch C6 are in a combined state, the driving shaft S1 drives the fixed gear Z2 to rotate, drives the floating gear Z15 to rotate, and then transmits power to the output shaft S9 through a first output path;
advancing in a 3-gear: when the clutch C1 and the clutch C7 are in a combined state, the driving shaft S1 drives the fixed gear Z1 to rotate, drives the fixed gear Z3 to rotate, drives the floating gear Z14 to rotate, drives the fixed gear Z7 to rotate, drives the fixed gear Z5 to rotate, and then transmits power to the output shaft S9 through a second output path;
advancing for 4 gears: the clutch C2 and the clutch C7 are in a combined state, the driving shaft S1 drives the fixed gear Z2 to rotate, drives the floating gear Z15 to rotate, and then transmits power to the output shaft S9 through a second output path;
advancing in 5 gears: the clutch C1 and the clutch C4 are in a combined state, the driving shaft S1 drives the fixed gear Z1 to rotate, drives the fixed gear Z3 to rotate, drives the floating gear Z14 to rotate, and then transmits power to the output shaft S9 through a third output path;
advancing for 6 gears: the clutch C2 and the clutch C4 are in a combined state, the driving shaft S1 drives the fixed gear Z2 to rotate, drives the floating gear Z15 to rotate, drives the fixed gear Z5 to rotate, and then transmits power to the output shaft S9 through a third output path;
advancing to 7 gears: the clutch C1 and the clutch C5 are in a combined state, the driving shaft S1 drives the fixed gear Z1 to rotate, drives the fixed gear Z3 to rotate, drives the floating gear Z14 to rotate, and then transmits power to the output shaft S9 through a fourth output path;
advancing for 8 gears: the clutch C2 and the clutch C5 are in a combined state, the driving shaft S1 drives the fixed gear Z2 to rotate, drives the floating gear Z15 to rotate, drives the fixed gear Z5 to rotate, and then transmits power to the output shaft S9 through a fourth output path;
backing off a 1 gear: the clutch C3 and the clutch C6 are in a combined state, the driving shaft S1 drives the fixed gear Z1 to rotate, drives the fixed gear Z6 to rotate, drives the floating gear Z16 to rotate, drives the fixed gear Z5 to rotate, and then transmits power to the output shaft S9 through a first output path;
backing off 2 gears: the clutch C3 and the clutch C7 are in a combined state, the driving shaft S1 drives the fixed gear Z1 to rotate, drives the fixed gear Z6 to rotate, drives the floating gear Z16 to rotate, drives the fixed gear Z5 to rotate, and then transmits power to the output shaft S9 through a second output path;
backing off 3 gears: the clutch C3 and the clutch C4 are in a combined state, the driving shaft S1 drives the fixed gear Z1 to rotate, drives the fixed gear Z6 to rotate, drives the floating gear Z16 to rotate, drives the fixed gear Z5 to rotate, and then transmits power to the output shaft S9 through a third output path;
4, backing off: the clutch C3 and the clutch C5 are in a combined state, the driving shaft S1 drives the fixed gear Z1 to rotate, drives the fixed gear Z6 to rotate, drives the floating gear Z16 to rotate, drives the fixed gear Z5 to rotate, and then transmits power to the output shaft S9 through a fourth output path; see table 1 for the above clutch engagement conditions.
TABLE 1 Clutch engagement status table for each gear in forward 8/reverse 4 modes
Figure 528012DEST_PATH_IMAGE002
In the forward 4-gear/reverse 4-gear mode, the intermediate shaft S2, the fixed gear Z3, the clutch C1 and the floating gear Z14 do not participate in transmission, wherein:
advancing to a 1 gear: the same as the transmission path of forward 2 gear in the forward 8-gear/reverse 4-gear mode;
advancing for 2 gears: the same as the transmission path of forward 4 gear in the forward 8-gear/reverse 4-gear mode;
advancing in a 3-gear: the same as the transmission path of forward 6 gear in the forward 8-gear/reverse 4-gear mode;
advancing for 4 gears: the same as the transmission path of forward 8 gear in the forward 8-gear/reverse 4-gear mode;
backing off a 1 gear: the same as the transmission path of reverse 1 gear in the forward 8-gear/reverse 4-gear mode;
backing off 2 gears: the same as the transmission path of reverse 2 gear in the forward 8-gear/reverse 4-gear mode;
backing off 3 gears: the same as the transmission path of reverse 3 gear in the forward 8-gear/reverse 4-gear mode;
4, backing off: the above clutch engagement is seen in table 2 as the reverse 4 gear transmission path in the forward 8/reverse 4 gear mode.
TABLE 2 Clutch engagement status table for each shift operating in Forward 4/reverse 4 modes
Figure 507469DEST_PATH_IMAGE004
In another embodiment, shown in fig. 5, for forward 4/reverse 4 modes:
the countershaft S3 is provided with a fixed gear Z23, the fixed gear Z23 is meshed with the fixed gear Z2, the countershaft S2, the fixed gear Z1, the fixed gear Z3, the clutch C1, the floating gear Z14 and the fixed gear Z6 do not participate in transmission, wherein:
advancing to a 1 gear: the same as the transmission path of forward 2 gear in the forward 8-gear/reverse 4-gear mode;
advancing for 2 gears: the same as the transmission path of forward 4 gear in the forward 8-gear/reverse 4-gear mode;
advancing in a 3-gear: the same as the transmission path of forward 6 gear in the forward 8-gear/reverse 4-gear mode;
advancing for 4 gears: the same as the transmission path of forward 8 gear in the forward 8-gear/reverse 4-gear mode;
backing off a 1 gear: the clutch C3 and the clutch C6 are in a combined state, the driving shaft S1 drives the fixed gear Z2 to rotate, drives the fixed gear Z23 to rotate, drives the floating gear Z16 to rotate, drives the fixed gear Z5 to rotate, and then transmits power to the output shaft S9 through a first output path;
backing off 2 gears: the clutch C3 and the clutch C7 are in a combined state, the driving shaft S1 drives the fixed gear Z2 to rotate, drives the fixed gear Z23 to rotate, drives the floating gear Z16 to rotate, drives the fixed gear Z5 to rotate, and then transmits power to the output shaft S9 through a second output path;
backing off 3 gears: the clutch C3 and the clutch C4 are in a combined state, the driving shaft S1 drives the fixed gear Z2 to rotate, drives the fixed gear Z23 to rotate, drives the floating gear Z16 to rotate, drives the fixed gear Z5 to rotate, and then transmits power to the output shaft S9 through a third output path;
4, backing off: when the clutch C3 and the clutch C5 are engaged, the driving shaft S1 rotates the fixed gear Z2, rotates the fixed gear Z23, rotates the floating gear Z16, rotates the fixed gear Z5, and transmits power to the output shaft S9 through the fourth output path, which is shown in table 2.
When the transmission is used as a multi-gear transmission, namely a forward 8-gear/reverse 4-gear mode, all shafts, all clutches and all gears in the design structure all participate in work, and naturally, the structure can realize the modes by controlling the combination of different clutch combinations, and the modes also comprise: a forward 7 speed, a forward 6 speed, a forward 5 speed, a forward 4 speed, a forward 3 speed, a forward 2 speed, a reverse 4 speed, a reverse 3 speed, and a reverse 2 speed, and a mode in which any one forward speed number and any one reverse speed number are combined. On the other hand, the forward 4-gear/reverse 4-gear modes can be realized under the working modes of all the structures, but the cost is high, the size is large, and the invention provides a novel low-gear mode which is simple and easy to implement and low in cost by removing partial structures in the original structure (the intermediate shaft S2 and the fixed gear Z3, the clutch C1 and the floating gear Z14 on the intermediate shaft S2 are removed in the embodiment).
In the gearbox of the technical scheme, through the layout of nine shafts, each shaft only has a clutch structure to realize the highest forward 8-gear/reverse 4-gear, the range of gear speed ratio can reach 0.5-8, and the speed ratio of each gear of the gearbox can be flexibly adjusted under the condition of not changing a transmission route; the few-gear mode can be realized by changing or removing part of the shaft and the structure on the shaft, namely, the total number of parts of the gearbox is reduced under the condition of not changing other structures, the modular design is realized, and the production cost and the use cost are reduced.
In conclusion, the gearbox in the technical scheme can realize the highest forward 8-gear and reverse 4-gear mode, meets the requirements of special machinery on 8 forward gears, can control different clutches to be combined, and can be adjusted to be the modes of forward 7-gear and reverse 3-gear, forward 6-gear and reverse 3-gear, forward 5-gear and reverse 3-gear and forward 4-gear and reverse 3-gear, and meets the requirements of different main machines on different gears; in addition, under the condition of not changing a transmission route, the speed ratio of each gear of the gearbox can be flexibly adjusted; secondly, under the condition that a box body of the gearbox is not changed, part of parts are changed or deleted, and different speed ratios and gear requirements are met; the gearbox body is kept unchanged, the modular design of the gearbox is realized, the generalization rate of parts of the gearbox is improved, and the production cost of the gearbox is reduced.
The above detailed description should not be construed as limiting the scope of the invention. Those skilled in the art will appreciate that various modifications, combinations, sub-combinations, and substitutions can occur, depending on design requirements and other factors. Any modification, equivalent replacement, and improvement made within the spirit and principle of the present invention should be included in the protection scope of the present invention.

Claims (5)

1. Modular design gearbox, including the box, its characterized in that still includes:
a drive shaft S1 on which a fixed gear Z1 and a fixed gear Z2 are provided;
an intermediate shaft S2 on which a fixed gear Z3 and a floating gear Z14 mounted by a clutch C1 are provided; the fixed gear Z3 meshes with the fixed gear Z1;
an intermediate shaft S4 on which a fixed gear Z4, a fixed gear Z5 and a floating gear Z15 mounted by a clutch C2 are provided; the floating gear Z15 is meshed with the fixed gear Z2;
an intermediate shaft S3 on which a fixed gear Z6 and a floating gear Z16 mounted by a clutch C3 are provided; the fixed gear Z6 is meshed with the fixed gear Z1, and the floating gear Z16 is meshed with the fixed gear Z5;
an intermediate shaft S5 on which a fixed gear Z7 and a floating gear Z17 mounted by a clutch C4 are provided; the fixed gear Z7 meshes with the floating gear Z14, and the fixed gear Z7 meshes with the fixed gear Z5;
an intermediate shaft S6 on which a fixed gear Z8 and a floating gear Z18 mounted by a clutch C5 are provided; the fixed gear Z8 is meshed with the fixed gear Z7, and the floating gear Z18 is meshed with the floating gear Z17;
an intermediate shaft S7 on which a fixed gear Z9, a fixed gear Z10 and a floating gear Z19 mounted by a clutch C6 are provided; the fixed gear Z9 meshes with the fixed gear Z4;
an intermediate shaft S8 on which is disposed fixed gear Z11 and a floating gear set mounted via clutch C7; the fixed gear Z11 meshes with the fixed gear Z10, and the floating gear set meshes with the floating gear Z19;
an output shaft S9 on which a fixed gear Z12 and a fixed gear Z13 are provided; the fixed gear Z12 is in mesh with the floating gear Z18, and the fixed gear Z13 is in mesh with the floating gear set;
in the forward mode, the drive shaft S1, the intermediate shaft S5, the intermediate shaft S7, and the output shaft S9 rotate in the same direction and in the opposite direction to the intermediate shaft S2, the intermediate shaft S4, the intermediate shaft S6, and the intermediate shaft S8;
in the reverse shift mode, the drive shaft S1, the intermediate shaft S4, the intermediate shaft S6, and the intermediate shaft S8 rotate in the same direction, and in the opposite direction to the rotation of the intermediate shaft S3, the intermediate shaft S5, the intermediate shaft S7, and the output shaft S9.
2. The modularly designed transmission of claim 1 wherein said floating gearset comprises a floating gear Z20 and a floating gear Z21 fixedly connected coaxially, said floating gear Z20 meshing with said floating gear Z19, said floating gear Z21 meshing with said fixed gear Z13; alternatively, the floating gear set includes only floating gear Z22, the floating gear Z22 is in mesh with the floating gear Z19, and the floating gear Z22 is in mesh with the fixed gear Z13.
3. A gear realization method for a modular design gearbox according to claim 1, characterized by the fact that it is used to realize a multi-gear mode comprising a forward 8/reverse 4 mode and a low-gear mode comprising a forward 4/reverse 4 mode;
when the clutch C6 is in the engaged state, a first output path is formed from the fixed gear Z4, through the fixed gear Z9, the floating gear Z19, the floating gear set, to the fixed gear Z13;
when the clutch C7 is in the engaged state, a second output path is formed from the fixed gear Z4, through the fixed gear Z9, the fixed gear Z10, the fixed gear Z11, the floating gear set, to the fixed gear Z13;
when the clutch C4 is in the engaged state, a third output path is formed from the fixed gear Z7, through floating gear Z17, the floating gear Z18, to the fixed gear Z12;
when the clutch C5 is in the engaged state, a fourth output path is formed from the fixed gear Z7, through the fixed gear Z8, the floating gear Z18, to the fixed gear Z12;
forward 8/reverse 4 mode wherein:
advancing to a 1 gear: the clutch C1 and the clutch C6 are engaged, and the driving shaft S1 rotates the fixed gear Z1, rotates the fixed gear Z3, rotates the floating gear Z14, rotates the fixed gear Z7, rotates the fixed gear Z5, and then transmits power to the output shaft S9 through the first output path;
advancing for 2 gears: the clutch C2 and the clutch C6 are engaged, and the driving shaft S1 rotates the fixed gear Z2, rotates the floating gear Z15, and transmits power to the output shaft S9 through the first output path;
advancing in a 3-gear: the clutch C1 and the clutch C7 are engaged, and the driving shaft S1 rotates the fixed gear Z1, rotates the fixed gear Z3, rotates the floating gear Z14, rotates the fixed gear Z7, rotates the fixed gear Z5, and then transmits power to the output shaft S9 through the second output path;
advancing for 4 gears: the clutch C2 and the clutch C7 are engaged, and the driving shaft S1 rotates the fixed gear Z2, rotates the floating gear Z15, and transmits power to the output shaft S9 through the second output path;
advancing in 5 gears: the clutch C1 and the clutch C4 are engaged, and the driving shaft S1 rotates the fixed gear Z1, rotates the fixed gear Z3, rotates the floating gear Z14, and then transmits power to the output shaft S9 via the third output path;
advancing for 6 gears: the clutch C2 and the clutch C4 are engaged, the driving shaft S1 rotates the fixed gear Z2, rotates the floating gear Z15, rotates the fixed gear Z5, and then transmits power to the output shaft S9 via the third output path;
advancing to 7 gears: the clutch C1 and the clutch C5 are engaged, and the driving shaft S1 rotates the fixed gear Z1, rotates the fixed gear Z3, rotates the floating gear Z14, and then transmits power to the output shaft S9 via the fourth output path;
advancing for 8 gears: the clutch C2 and the clutch C5 are engaged, the driving shaft S1 rotates the fixed gear Z2, rotates the floating gear Z15, rotates the fixed gear Z5, and then transmits power to the output shaft S9 via the fourth output path;
backing off a 1 gear: the clutch C3 and the clutch C6 are engaged, and the driving shaft S1 rotates the fixed gear Z1, rotates the fixed gear Z6, rotates the floating gear Z16, rotates the fixed gear Z5, and then transmits power to the output shaft S9 through the first output path;
backing off 2 gears: the clutch C3 and the clutch C7 are engaged, and the driving shaft S1 rotates the fixed gear Z1, rotates the fixed gear Z6, rotates the floating gear Z16, rotates the fixed gear Z5, and then transmits power to the output shaft S9 through the second output path;
backing off 3 gears: the clutch C3 and the clutch C4 are engaged, and the driving shaft S1 rotates the fixed gear Z1, rotates the fixed gear Z6, rotates the floating gear Z16, rotates the fixed gear Z5, and then transmits power to the output shaft S9 through the third output path;
4, backing off: the clutch C3 and the clutch C5 are engaged, and the driving shaft S1 rotates the fixed gear Z1, rotates the fixed gear Z6, rotates the floating gear Z16, rotates the fixed gear Z5, and then transmits power to the output shaft S9 through the fourth output path;
in forward 4/reverse 4 mode, none of the countershaft S2, the fixed gear Z3, the clutch C1, and the floating gear Z14 are engaged in drive, wherein:
advancing to a 1 gear: the transmission path is the same as that of the forward 2 gear in the forward 8-gear/reverse 4-gear mode;
advancing for 2 gears: the transmission path is the same as that of the forward 4 gear in the forward 8-gear/reverse 4-gear mode;
advancing in a 3-gear: the transmission path is the same as that of the forward 6 gear in the forward 8-gear/reverse 4-gear mode;
advancing for 4 gears: the transmission path is the same as that of the forward 8 gear in the forward 8-gear/reverse 4-gear mode;
backing off a 1 gear: the same as the transmission path of reverse 1 gear in the forward 8-gear/reverse 4-gear mode;
backing off 2 gears: the transmission path is the same as that of the reverse 2 gear in the forward 8-gear/reverse 4-gear mode;
backing off 3 gears: the same as the transmission path of reverse 3 gear in the forward 8-gear/reverse 4-gear mode;
4, backing off: the same as the reverse 4-speed transmission path in the forward 8-speed/reverse 4-speed mode.
4. The method of claim 3, wherein the floating gear set comprises a floating gear Z20 and a floating gear Z21 which are coaxially and fixedly connected, the floating gear Z20 is meshed with the floating gear Z19, and the floating gear Z21 is meshed with the fixed gear Z13; alternatively, the floating gear set includes only floating gear Z22, the floating gear Z22 is in mesh with the floating gear Z19, and the floating gear Z22 is in mesh with the fixed gear Z13.
5. A gear realization method for a modular design gearbox according to claim 3, characterized in that the forward 4/reverse 4 mode can also be realized by:
fixed gear Z23 is disposed on the countershaft S3, the fixed gear Z23 is meshed with the fixed gear Z2, none of the countershaft S2, the fixed gear Z1, the fixed gear Z3, the clutch C1, the floating gear Z14 and the fixed gear Z6 participate in transmission, wherein:
advancing to a 1 gear: the transmission path is the same as that of the forward 2 gear in the forward 8-gear/reverse 4-gear mode;
advancing for 2 gears: the transmission path is the same as that of the forward 4 gear in the forward 8-gear/reverse 4-gear mode;
advancing in a 3-gear: the transmission path is the same as that of the forward 6 gear in the forward 8-gear/reverse 4-gear mode;
advancing for 4 gears: the transmission path is the same as that of the forward 8 gear in the forward 8-gear/reverse 4-gear mode;
backing off a 1 gear: the clutch C3 and the clutch C6 are engaged, and the driving shaft S1 rotates the fixed gear Z2, rotates the fixed gear Z23, rotates the floating gear Z16, rotates the fixed gear Z5, and then transmits power to the output shaft S9 through the first output path;
backing off 2 gears: the clutch C3 and the clutch C7 are engaged, and the driving shaft S1 rotates the fixed gear Z2, rotates the fixed gear Z23, rotates the floating gear Z16, rotates the fixed gear Z5, and then transmits power to the output shaft S9 through the second output path;
backing off 3 gears: the clutch C3 and the clutch C4 are engaged, and the driving shaft S1 rotates the fixed gear Z2, rotates the fixed gear Z23, rotates the floating gear Z16, rotates the fixed gear Z5, and then transmits power to the output shaft S9 through the third output path;
4, backing off: the clutch C3 and the clutch C5 are engaged, and the driving shaft S1 rotates the fixed gear Z2, rotates the fixed gear Z23, rotates the floating gear Z16, rotates the fixed gear Z5, and then transmits power to the output shaft S9 through the fourth output path.
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