CN101055024A - Commutation mechanism for vehicle gear box - Google Patents

Commutation mechanism for vehicle gear box Download PDF

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Publication number
CN101055024A
CN101055024A CNA2007100777636A CN200710077763A CN101055024A CN 101055024 A CN101055024 A CN 101055024A CN A2007100777636 A CNA2007100777636 A CN A2007100777636A CN 200710077763 A CN200710077763 A CN 200710077763A CN 101055024 A CN101055024 A CN 101055024A
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CN
China
Prior art keywords
planet
planet row
gear
clutch
gear ring
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
CNA2007100777636A
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Chinese (zh)
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CN100480540C (en
Inventor
舒瑞龙
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Guizhou Winstar Hydraulic Transmission Machinery Co Ltd
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Guizhou Winstar Hydraulic Transmission Machinery Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
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Application filed by Guizhou Winstar Hydraulic Transmission Machinery Co Ltd filed Critical Guizhou Winstar Hydraulic Transmission Machinery Co Ltd
Priority to CNB2007100777636A priority Critical patent/CN100480540C/en
Publication of CN101055024A publication Critical patent/CN101055024A/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
    • F16H3/44—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
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
    • F16H2200/0034—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising two 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
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
    • F16H2200/2007—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with two sets of orbital gears
    • 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
    • F16H2200/2035—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with two engaging means

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

Abstract

The present invention discloses a changement for a vehicle speed changing box, planet frame braking and gear ring output, wherein the sun gears of a first planet row, the sun gears of a second planet row, and a clutch are connected to an input shaft, the clutch and an arrester are connected to the planet frame of the first planet row, the gear ring of the first planet row is connected to the planet frame of the second planet row, the gear ring of the second planet row is connected to the output shaft. The invention has less power loss, little force applied on the planet gear, compensates the fault of the existing changement, can realize the drive with a forward direction speed ratio is 1 and an inverse direction speed ratio is -0.56 to -1.78, is compact and simple in structure, and can be combined with torque converter and speed-changer in series, and can form a hydraulic speed-changer having same forward gear and backward gear.

Description

Commutation mechanism for vehicle gear box
Technical field:
The present invention relates to a kind of commutation mechanism for vehicle gear box, particularly a kind of tractor, engineering machinery vehicle gearbox changement.
Background technique:
In the hydraudynamic drive machinery of some whole gear band reverse gear, as crawler tractor, construction machinery gear box often is provided with special changement, modern changement is realized commutating with clutch or break, it is identical with the backward gear number to advance, and the speed of a motor vehicle is identical or close, and commutation process is fast.Existing crawler tractor commutation fixed shaft type or the double star planet row structures of adopting more, for example " vehicle hydraulic transmission " National Defense Industry Press front page in June nineteen eighty-three has just been introduced Caterpillar crawler tractor changement for the 392nd page, this changement adopts double star planet row structure, relative complex.Introduced the Allison engineering machinery respectively with torque converter CRT3531 and CRT5633 three first three torque converter mechanisms of falling the 385th page and the 389th page of " vehicle hydraulic transmission " National Defense Industry Press front page in June nineteen eighty-three equally, the gear ring that oppositely all adopts of the changement of its speed changer is braked, planet carrier output, its planet wheel stressed bigger, power loss is also bigger.
Summary of the invention:
The objective of the invention is to provides a kind of special changement to vehicle gear box, to obtain the close positive decommuntation of speed ratio.Single star planet row changement provided by the invention adopts the planet carrier braking, and gear ring is passive, and is not only simple in structure, and it is stressed big to solve in the prior art planet wheel, the defective that power loss is big.
The basic building block of changement of the present invention comprises two groups of single star planet rows, and clutch and break also have input shaft, output shaft.Two groups of single star planet rows' sun gear all links to each other with input shaft, clutch links to each other with input shaft, first planet row's planet carrier connects break and clutch, and first planet row's gear ring connects second planet row's planet carrier, and second planet row's gear ring connects output shaft.
The principle of this changement: when in conjunction with clutch, first planet row and second planet row is whole rotates together with input shaft, the gear ring that second planet that connects together with output shaft is arranged will drive output shaft and rotate.Output shaft is identical with the sense of rotation of input shaft, and speed ratio is 1.When in conjunction with break, first planet row's planet carrier braking, first planet row's sun gear drives first planet row's planet wheel with the opposite direction rotation of input shaft, the gear ring that drives first planet row thus is also with the opposite direction rotation of input shaft, and the planet carrier and the planet wheel that drive second planet row also rotate with the opposite direction of input shaft, meanwhile second planet row's sun gear drives second planet row's planet wheel with the opposite direction rotation of input shaft, therefore second planet row's planet wheel drives second planet row's gear ring rotation with the opposite sense of rotation of input shaft, second planet row's who connects together with output shaft gear ring will drive output shaft also with the opposite direction rotation of input shaft, and speed ratio is-α 1* α 2/ (α 1+ α 2+1).Wherein α 1 is first planet row's structural parameter, and α 2 is second planet row's structural parameter, by the different teeth of joining, can obtain reverse speed ratio and be-0.56 to-1.78 transmission.
Compared with prior art, planet wheel relative rotation speed of the present invention is little, and it is less that planet wheel bears moment of torsion, and less, the total transmission efficiency height of planet row's relative power with torque-converters, gearbox tandem compound, can be formed the torque converter with identical forward gears and backward gear.
Description of drawings:
Fig. 1 is a driver composition of the present invention
Fig. 2 is the invention structural representation
Embodiment:
By Fig. 1 and Fig. 2 as can be known, the structure of this changement has input shaft 1, the output shaft 19 coaxial with input shaft 1, clutch L and break Z, two groups of single star planets row P1 and P2.
First planet is arranged P1, belongs to single star planet row, comprises sun gear 10, and the gear ring 13 of band internal tooth is with the planet wheel 12 of sun gear 10 and gear ring 13 engagements and the planet carrier 11 of support planet wheel 12; Second planet is arranged P2, belongs to single star planet row, comprises sun gear 15, and the gear ring 17 of band internal tooth is with the planet wheel 16 of sun gear 15 and gear ring 17 engagements and the planet carrier 14 of support planet wheel 16.
Clutch L comprises clutch friction plate 3, and break Z comprises brake bush 7.
Wherein input shaft 1 is with the internal tooth engagement of clutch oil cylinder 2, outer hub 4 engagements of the outer heel clutch of clutch oil cylinder 2, the external tooth of clutch friction plate 3 also meshes with the outer hub 4 of clutch simultaneously, brake bush 7 is fixed on the housing 9 by fixed plate 6, and the external tooth of hub 5 meshes with the internal tooth of clutch friction plate 4, the internal tooth of brake bush 7 respectively; The internal tooth of planet carrier 11 engagement hubs 5, gear ring 13 splines connect planet carrier 14, the external tooth of drum 18 and gear ring 17 engagements, the internal tooth of drum 18 and output shaft 19 engagements, sun gear 10 and sun gear 15 are installed on the input shaft 1.
The structure that two single star planets of present embodiment are arranged each member is identical, and wherein the number of teeth of sun gear 10 and sun gear 15 is 42, and the number of teeth of gear ring 13 and gear ring 17 is 102, and the number of planet wheel 12 and planet wheel 16 is four.
By solenoidoperated cluthes L, the combination of break Z or separation realize that the forward speed ratio is 1, and oppositely speed ratio is-1 transmission.
If the rotating speed of input shaft 1 is no, when clutch L in conjunction with the time, relative rotation speed between each planet wheel of first planet row P1 and second planet row P2 all is 0, when break Z in conjunction with the time, the rotating speed of planet wheel 12 relative planet carriers 11 is 1.4no, the rotating speed of planet wheel 16 relative planet carriers 14 is 1.976no, and the stressed relative prior art of planet wheel 12 and planet wheel 16 obviously reduces.
When getting the internal gear pair transmission efficiency is 0.99, external gear pump auxiliary driving efficient is 0.98, when input power is P, first planet row P1 relative power is 0.58P, second planet row P2 relative power is 0.58P, so 19 transmission efficiency is 0.9654 from input shaft 1 to output shaft, power loss is almost half of prior art.

Claims (2)

1, a kind of commutation mechanism for vehicle gear box, has a clutch (L), a break (Z), first planet row (P1), second planet row (P2), input shaft (1) and output shaft (19), it is characterized in that: input shaft (1) is successively by clutch oil cylinder (2), the outer hub (4) of clutch connects clutch (L), clutch (L) is connected by the planet carrier (11) of hub (5) with first planet row (P1) with break (Z), first planet row's (P1) sun gear (10) and second planet row's (P2) sun gear (15) all meshes with input shaft (1), first planet row's (P1) gear ring (13) engagement second planet row's (P2) planet carrier (14), second planet row's (P2) gear ring (17) connects output shaft (19) by drum (18).
2, changement according to claim 1, it is characterized in that described first planet row's (P1) the sun gear (10) and described second planet row's (P2) sun gear (15) number of teeth all are 42, the number of teeth of gear ring (13) and gear ring (17) all is 102.
CNB2007100777636A 2007-05-14 2007-05-14 Commutation mechanism for vehicle gear box Active CN100480540C (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CNB2007100777636A CN100480540C (en) 2007-05-14 2007-05-14 Commutation mechanism for vehicle gear box

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CNB2007100777636A CN100480540C (en) 2007-05-14 2007-05-14 Commutation mechanism for vehicle gear box

Publications (2)

Publication Number Publication Date
CN101055024A true CN101055024A (en) 2007-10-17
CN100480540C CN100480540C (en) 2009-04-22

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Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102644714A (en) * 2012-04-19 2012-08-22 燕山大学 Continuous variable phase transmission mechanism of interruptable homodromous variable speed planetary gear trains
CN102644712A (en) * 2012-04-19 2012-08-22 燕山大学 Continuous variable phase transmission mechanism of interruptable reverse variable speed planetary gear trains
CN102644711A (en) * 2012-04-19 2012-08-22 燕山大学 Continuous variable phase transmission mechanism of interruptable reverse variable speed planetary gear trains
CN102797825A (en) * 2012-08-27 2012-11-28 项子澄 Vehicular closed self-circulation differential infinitely variable speed transmission gearbox
CN103697121A (en) * 2013-12-19 2014-04-02 贵州凯星液力传动机械有限公司 Multi-gear reduction transmission device for engineering machinery equipment
CN106838154A (en) * 2016-12-14 2017-06-13 山推工程机械股份有限公司 A kind of manual transmission
CN107100976A (en) * 2017-04-25 2017-08-29 天津工程机械研究院有限公司 A kind of forward and reverse dynamic power shift gear box of hydraulic hybrid power loader
CN107830144A (en) * 2017-12-18 2018-03-23 山东华山拖拉机制造有限公司 Tractor automatic gear shifting dynamic gearshift
CN109681593A (en) * 2018-11-29 2019-04-26 中国北方车辆研究所 A kind of double internal messing Zheng Dao mechanism
CN110657202A (en) * 2018-06-29 2020-01-07 比亚迪股份有限公司 Transmission, power driving system and vehicle
CN112747088A (en) * 2019-10-29 2021-05-04 中车时代电动汽车股份有限公司 New energy automobile and derailleur and gear drive structure thereof
CN113719588A (en) * 2021-09-10 2021-11-30 贵州凯星液力传动机械有限公司 Double-inner-gearing two-gear speed change mechanism

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102606716A (en) * 2012-03-28 2012-07-25 浙江长泰机械有限公司 Transfer case of high-power tractor

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB581534A (en) * 1944-08-31 1946-10-16 Paxman & Co Ltd Davey Improvements in or relating to reversible transmission gears for engines
GB1284548A (en) * 1968-09-09 1972-08-09 Nippon Denso Co Automatic transmission
US3713351A (en) * 1969-09-27 1973-01-30 Toyota Motor Co Ltd Electrical automatic shift control system with hilly country detecting unit
CN100362261C (en) * 2005-11-24 2008-01-16 贵州凯星液力传动机械有限公司 Transmission for hydraulic variable speed device
CN1912422A (en) * 2006-08-10 2007-02-14 高安平 Superstage automatic speed transmission

Cited By (20)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102644714A (en) * 2012-04-19 2012-08-22 燕山大学 Continuous variable phase transmission mechanism of interruptable homodromous variable speed planetary gear trains
CN102644712A (en) * 2012-04-19 2012-08-22 燕山大学 Continuous variable phase transmission mechanism of interruptable reverse variable speed planetary gear trains
CN102644711A (en) * 2012-04-19 2012-08-22 燕山大学 Continuous variable phase transmission mechanism of interruptable reverse variable speed planetary gear trains
CN102644711B (en) * 2012-04-19 2014-08-06 燕山大学 Continuous variable phase transmission mechanism of interruptable reverse variable speed planetary gear trains
CN102644712B (en) * 2012-04-19 2014-09-10 燕山大学 Continuous variable phase transmission mechanism of interruptable reverse variable speed planetary gear trains
CN102644714B (en) * 2012-04-19 2015-01-07 燕山大学 Continuous variable phase transmission mechanism of interruptable homodromous variable speed planetary gear trains
CN102797825A (en) * 2012-08-27 2012-11-28 项子澄 Vehicular closed self-circulation differential infinitely variable speed transmission gearbox
CN103697121A (en) * 2013-12-19 2014-04-02 贵州凯星液力传动机械有限公司 Multi-gear reduction transmission device for engineering machinery equipment
CN103697121B (en) * 2013-12-19 2016-08-17 贵州凯星液力传动机械有限公司 A kind of engineering mechanical device many gears speed reduction gearing
CN106838154A (en) * 2016-12-14 2017-06-13 山推工程机械股份有限公司 A kind of manual transmission
CN107100976A (en) * 2017-04-25 2017-08-29 天津工程机械研究院有限公司 A kind of forward and reverse dynamic power shift gear box of hydraulic hybrid power loader
CN107100976B (en) * 2017-04-25 2023-07-07 天津工程机械研究院有限公司 Forward and reverse power gear shifting gearbox for hydraulic hybrid loader
CN107830144A (en) * 2017-12-18 2018-03-23 山东华山拖拉机制造有限公司 Tractor automatic gear shifting dynamic gearshift
CN110657202A (en) * 2018-06-29 2020-01-07 比亚迪股份有限公司 Transmission, power driving system and vehicle
CN110657202B (en) * 2018-06-29 2022-03-15 比亚迪股份有限公司 Transmission, power driving system and vehicle
CN109681593A (en) * 2018-11-29 2019-04-26 中国北方车辆研究所 A kind of double internal messing Zheng Dao mechanism
CN109681593B (en) * 2018-11-29 2020-11-20 中国北方车辆研究所 Double-inner-meshing forward and backward mechanism
CN112747088A (en) * 2019-10-29 2021-05-04 中车时代电动汽车股份有限公司 New energy automobile and derailleur and gear drive structure thereof
CN112747088B (en) * 2019-10-29 2022-09-13 中车时代电动汽车股份有限公司 New energy automobile and derailleur and gear drive structure thereof
CN113719588A (en) * 2021-09-10 2021-11-30 贵州凯星液力传动机械有限公司 Double-inner-gearing two-gear speed change mechanism

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