CN201155550Y - Dynamic gear shifting transmission-gear box suitable for engineering machinery - Google Patents
Dynamic gear shifting transmission-gear box suitable for engineering machinery Download PDFInfo
- Publication number
- CN201155550Y CN201155550Y CNU2008200622404U CN200820062240U CN201155550Y CN 201155550 Y CN201155550 Y CN 201155550Y CN U2008200622404 U CNU2008200622404 U CN U2008200622404U CN 200820062240 U CN200820062240 U CN 200820062240U CN 201155550 Y CN201155550 Y CN 201155550Y
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- China
- Prior art keywords
- gear
- shaft
- clutch
- jack shaft
- jack
- 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.)
- Expired - Fee Related
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Classifications
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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
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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
- F16H2003/0935—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 with multiple countershafts comprising only one idle gear and one gear fixed to the countershaft
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Structure Of Transmissions (AREA)
Abstract
The utility model relates to a power shift gear box which is fit for engineering machinery. The power shaft gear box mainly solves the problem of the prior gear box used for the engineering machinery which has a plurality of parts and a complex transmission circuit. The power shift gear box consists of an input shaft, an output shaft, a plurality of shaft, a plurality of clutches and a plurality of gears; wherein, a plurality of gears form a reversing gear set; the other gears form a driver gear set; if viewing from the end face along the transmission circuit of the shafts, the input shaft (16), and a second and a sixth middle shafts (18 and 22) are arranged in a triangular shape, the input shaft (16) and a first, a third and the sixth middle shafts (17, 19 and 22) are arranged in a quadrangular shape; the output shaft (23) and the third, a fourth and a fifth middle shafts 19, 20 and 21) are arranged in the quadrangular shape. After the structure is used, the transmission circuit is more impact, and the power shift gear box has less parts and higher transmission efficiency.
Description
Technical field
The utility model relates to a kind of Powershift transmission that is applicable to engineering machinery, the particularly Powershift transmission of loader, grader.
Background technique
Present engineering machinery, as wheel loader, grader, dumping car, gearbox on the excavator has two kinds of planetary and fixed shaft types usually, adopt planetary gearbox, its processed complex, the required precision height, gear is few, transmission efficiency is low, and manufacture cost height, the disclosed a kind of multispeed powershift ahead running gearbox that can gear shift under load of another kind of fixed axle gearbox such as Chinese utility application prospectus CN1068939C, this gearbox two clutches of one grade of needs that advance, ten gears and six engagements could realize power output, yet the one grade of general utilization rate of advancing is higher, be about about 30%, the number of times of transmission process gear quantity and engagement is many more, to directly cause transmission efficiency to descend and the parts depreciation increasing, maintenance expenses increases; This gearbox has 16 gears of eight axles and 6 clutches simultaneously, and its part is more, and corresponding manufacture cost is higher, and maintenance is inconvenience also.Accompanying drawing 4 is wherein a kind of fixed axle gearbox end face topological project, as can be seen, by the drive path of axle, sees triangle of each axle center composition from end face, and two four limit row are straight line at last, and transmission line is long, and transmission efficiency is obviously not high.
The model utility content
The utility model is many and drive path complicated problems at present gearbox part, provides a kind of part few, the Powershift transmission that is applicable to engineering machinery of compact structure.
For addressing the above problem, Powershift transmission of the present utility model is by an input shaft, an output shaft, some jack shafts and some clutches and gear are formed, the some of them gear constitutes commutating tooth wheels, other gears constitute a driving gear set, the fixed gear while and first jack shaft 17 on the described input shaft, second jack shaft 18, three free gear permanent engagement on the 6th jack shaft 22, fixed gear permanent engagement on fixed gear on second jack shaft 18 and the 6th jack shaft 22, the fixed gear while and first jack shaft 17 on the 3rd jack shaft 19, two fixed gears on the 6th jack shaft 22 and the 4th jack shaft 20, two free gear permanent engagement on the 5th jack shaft 21, fixed gear on the output shaft and the 4th jack shaft 20, two fixed gear permanent engagement on the 5th jack shaft 21, output shaft is positioned at gearbox bottom, drive path by axle, see input shaft and the second and the 6th jack shaft 18 from end face, 22 are triangularly arranged, input shaft is also with first, the 3rd, the 6th jack shaft 17,19,22 are four limit row arranges output shaft and the 3rd, the the 4th and the 5th jack shaft 19,20,21 are quadrangular array.
The forward gears of described gearbox is closed and four gear engagement realizations by two clutches, retreat shelves closed and five gear engagement realizations by two clutches, this gearbox has eight axles, each shaftgear adds up to 14, a fixed gear respectively is housed on input shaft and the output shaft, a free gear, a fixed gear and a clutch are housed on the every jack shaft, and this gearbox has six forward gearss and three to retreat shelves.
For a kind of improvement of the present utility model, can on the part transmission shaft of described gearbox, add the velocity ratio expansion that one or more gears are realized wider range.
Adopt the arrangement and the kind of drive of above input, output shaft jack shaft peripheral with it, the number of gears of the prior art can be reduced to 14 by 16, reduce manufacture cost, forward gears reduces to four engagements by six engagements, the minimizing of the required gear engagement number of times of transmission can make power transmission more effective, and accessory loss also can obviously reduce; After adopting this mode in addition, shortened its drive path, gearbox designs is compact more, and transmission efficiency is higher.
Description of drawings
Fig. 1 is the utility model end face topology diagram.
Fig. 2 is a transmission schematic representation of the present utility model.
Fig. 3 is a velocity ratio expansion schematic representation of the present utility model.
Fig. 4 is a kind of gearbox end face topology diagram of the prior art.
Embodiment
By Figure 1 and Figure 2, the utility model is by an input shaft 16, an output shaft 23, some jack shafts 17,18,19,20,21,22 and some clutches 24,25,26,27,28,29 and gear 2,3,4,5,6,7,8,9,10,11,12,13,14,15 form, wherein input shaft 16 and some jack shafts 17,18,22 and on gear 2,3,4,5,6,9,10 constitute commutating tooth wheels, jack shaft 19,20,21,23 and on gear 7,8,11,12,13,14,15 form a driving gear set, 2 whiles and first jack shaft 17 of fixed gear on the described input shaft 16, second jack shaft 18, three free gears 4 on the 6th jack shaft 22,6,10 permanent engagement, fixed gear 9 permanent engagement on fixed gear 5 on second jack shaft 18 and the 6th jack shaft 22,7 whiles and first jack shaft 17 of fixed gear on the 3rd jack shaft 19, two fixed gears 3 on the 6th jack shaft 22, the 9 and the 4th jack shaft 20, two free gears 13 on the 5th jack shaft 21,11 permanent engagement, fixed gear 15 on the output shaft 23 and the 4th jack shaft 20, two fixed gears 14 on the 5th jack shaft 21,12 permanent engagement, output shaft 23 is positioned at gearbox bottom, drive path by axle, see input shaft 16 and the second and the 6th jack shaft 18 from end face, 22 are triangularly arranged, input shaft 16 is also with first, the 3rd, the 6th jack shaft 17,19,22 are four limit row arranges output shaft 23 and the 3rd, the the 4th and the 5th jack shaft 19,20,21 are quadrangular array.
The forward gears of described gearbox is closed and four gear engagement realizations by two clutches, retreat shelves closed and five gear engagement realizations by two clutches.
Described gearbox has eight axles, and each shaftgear adds up to 14, on input shaft 16 and the output shaft 23 fixed gear is housed respectively, and a free gear, a fixed gear and a clutch are housed on the every jack shaft 17,18,19,20,21,22.
Described gearbox has six forward gearss, and three retreat shelves, and its embodiment is as follows:
First forward gears is by closed clutch 24 and clutch 26, gear 2 and gear 4 engagements, gear 3 and gear 7 engagements, gear 8 and gear 12 engagements, gear 12 and gear 15 engagements, power is delivered on the output shaft 23 by input shaft 16 driven gears 2,4,3,7,8,12,15.
The second gear that advances is by closed clutch 24 and clutch 27, gear 2 and gear 4 engagements, gear 3 and gear 7 engagements, gear 7 and gear 13 engagements, gear 14 and gear 15 engagements, power is delivered on the output shaft 23 by input shaft 16 driven gears 2,4,3,7,13,14,15.
The third gear of advancing is by closed clutch 24 and clutch 28, gear 2 and gear 4 engagements, gear 3 and gear 7 engagements, gear 7 and gear 11 engagements, gear 12 and gear 15 engagements, power is delivered on the output shaft 23 by input shaft 16 driven gears 2,4,3,7,11,12,15.
The fourth gear of advancing is by closed clutch 29 and clutch 26, gear 2 and gear 10 engagements, gear 9 and gear 7 engagements, gear 8 and gear 12 engagements, gear 12 and gear 15 engagements, power is delivered on the output shaft 23 by input shaft 16 driven gears 2,10,9,7,8,12,15.
Advance five grades by closed clutch 29 and clutch 27, gear 2 and gear 10 engagements, gear 9 and gear 7 engagements, gear 7 and gear 13 engagements, gear 14 and gear 15 engagements, power is delivered on the output shaft 23 by input shaft 16 driven gears 2,10,9,7,13,14,15.
Advance six grades by closed clutch 29 and clutch 28, gear 2 and gear 10 engagements, gear 9 and gear 7 engagements, gear 7 and gear 11 engagements, gear 12 and gear 15 engagements, power is delivered on the output shaft 23 by input shaft 16 driven gears 2,10,9,7,11,12,15.
The slow astern shelves are by closed clutch 25 and clutch 26, gear 2 and gear 6 engagements, gear 5 and gear 9 engagements, gear 9 and gear 7 engagements, gear 8 and gear 12 engagements, gear 12 and gear 15 engagements, power is delivered on the output shaft 23 by input shaft 16 driven gears 2,6,5,9,7,8,12,15.
Retreat second gear by closed clutch 25 and clutch 27, gear 2 and gear 6 engagements, gear 5 and gear 9 engagements, gear 9 and gear 7 engagements, gear 7 and gear 13 engagements, gear 14 and gear 15 engagements, power is delivered on the output shaft 23 by input shaft 16 driven gears 2,6,5,9,7,13,14,15.
Retreat third gear by closed clutch 25 and clutch 28, gear 2 and gear 6 engagements, gear 5 and gear 9 engagements, gear 9 and gear 7 engagements, gear 7 and gear 11 engagements, gear 12 and gear 15 engagements, power is delivered on the output shaft 23 by input shaft 16 driven gears 2,6,5,9,7,11,12,15.
Fig. 3 is a scheme of described gearbox velocity ratio expansion, has increased a fixed gear 30 on jack shaft 19, fixed gear 30 and fixed gear 9 and free gear 13 engagements, thus realize the velocity ratio expansion.
Claims (5)
1, be applicable to the Powershift transmission of engineering machinery, by an input shaft (16), an output shaft (23), some jack shafts (17,18,19,20,21,22) and some clutches (24,25,26,27,28,29) and gear (2,3,4,5,6,7,8,9,10,11,12,13,14,15) form, wherein input shaft (16) and some jack shafts (17,18,22) and on gear (2,3,4,5,6,9,10) constitute commutating tooth wheels, output shaft (23) and jack shaft (19,20,21) and on gear (7,8,11,12,13,14,15) form a driving gear set, it is characterized in that: fixed gear (2) while and first jack shaft (17) on the input shaft (16), second jack shaft (18), three free gears (4,6,10) permanent engagement on the 6th jack shaft (22), fixed gear (9) permanent engagement on fixed gear (5) on second jack shaft (18) and the 6th jack shaft (22), fixed gear (7) while and first jack shaft (17) on the 3rd jack shaft (19), two fixed gears (3,9) on the 6th jack shaft (22) and the 4th jack shaft (20), two free gears (13,11) permanent engagement on the 5th jack shaft (21), fixed gear (15) on the output shaft (23) and the 4th jack shaft (20), two fixed gears (14 on the 5th jack shaft (21), 12) permanent engagement, output shaft (23) is positioned at gearbox bottom, by the drive path of axle, see input shaft (16) and the second and the 6th jack shaft (18 from end face, 22) be triangularly arranged, input shaft (16) is also with first, the 3rd, the 6th jack shaft (17,19,22) being four limit row arranges, output shaft (23) and the 3rd, the the 4th and the 5th jack shaft (19,20,21) is quadrangular array.
2, according to the described Powershift transmission that is applicable to engineering machinery of claim 1, it is characterized in that: the forward gears of this gearbox is closed and four gear engagement realizations by two clutches, retreat shelves closed and five gear engagement realizations by two clutches.
3, according to the described Powershift transmission that is applicable to engineering machinery of claim 1, it is characterized in that: this gearbox has eight axles, each shaftgear adds up to 14, a fixed gear respectively is housed, every jack shaft (17,18 on input shaft (16) and the output shaft (23), 19, a free gear, a fixed gear and a clutch are housed 20,21,22).
4, according to the described Powershift transmission that is applicable to engineering machinery of claim 1, it is characterized in that: this gearbox has six forward gearss and three to retreat shelves, closed clutch (24) and clutch (26) are for advancing one grade, closed clutch (24) and clutch (27) are the second gear that advances, closed clutch (24) and clutch (28) are the third gear of advancing, closed clutch (29) and clutch (26) are the fourth gear of advancing, closed clutch (29) and clutch (27) are for advancing five grades, closed clutch (29) and clutch (28) are for advancing six grades, closed clutch (25) and clutch (26) are the slow astern shelves, closed clutch (25) and clutch (27) are for retreating second gear, and closed clutch (25) and clutch (28) are for retreating third gear.
5, according to the described Powershift transmission that is applicable to engineering machinery of claim 1, it is characterized in that: can realize the velocity ratio expansion of wider range by on the part transmission shaft, adding one or more gears.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNU2008200622404U CN201155550Y (en) | 2008-02-22 | 2008-02-22 | Dynamic gear shifting transmission-gear box suitable for engineering machinery |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNU2008200622404U CN201155550Y (en) | 2008-02-22 | 2008-02-22 | Dynamic gear shifting transmission-gear box suitable for engineering machinery |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN201155550Y true CN201155550Y (en) | 2008-11-26 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNU2008200622404U Expired - Fee Related CN201155550Y (en) | 2008-02-22 | 2008-02-22 | Dynamic gear shifting transmission-gear box suitable for engineering machinery |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN201155550Y (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101240832B (en) * | 2008-02-22 | 2010-06-02 | 四川成都成工工程机械股份有限公司 | Dynamic gear shifting transmission-gear box suitable for engineering machinery |
| EP2481949A1 (en) * | 2011-01-31 | 2012-08-01 | Deere & Company | Powertrain comprising a three speed transmission |
| CN111734792A (en) * | 2020-06-04 | 2020-10-02 | 江苏汇智高端工程机械创新中心有限公司 | Engineering machinery power gear shifting gearbox |
-
2008
- 2008-02-22 CN CNU2008200622404U patent/CN201155550Y/en not_active Expired - Fee Related
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101240832B (en) * | 2008-02-22 | 2010-06-02 | 四川成都成工工程机械股份有限公司 | Dynamic gear shifting transmission-gear box suitable for engineering machinery |
| EP2481949A1 (en) * | 2011-01-31 | 2012-08-01 | Deere & Company | Powertrain comprising a three speed transmission |
| US8522634B2 (en) | 2011-01-31 | 2013-09-03 | Deere & Company | Powertrain comprising a three speed transmission |
| CN111734792A (en) * | 2020-06-04 | 2020-10-02 | 江苏汇智高端工程机械创新中心有限公司 | Engineering machinery power gear shifting gearbox |
| CN111734792B (en) * | 2020-06-04 | 2021-07-09 | 江苏汇智高端工程机械创新中心有限公司 | Engineering machinery power gear shifting gearbox |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| C17 | Cessation of patent right | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20081126 Termination date: 20140222 |