CN107061639A - A kind of centre-to-centre spacing optimization method, gearbox and the vehicle of parallel axes system - Google Patents
A kind of centre-to-centre spacing optimization method, gearbox and the vehicle of parallel axes system Download PDFInfo
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- CN107061639A CN107061639A CN201710237541.XA CN201710237541A CN107061639A CN 107061639 A CN107061639 A CN 107061639A CN 201710237541 A CN201710237541 A CN 201710237541A CN 107061639 A CN107061639 A CN 107061639A
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- 238000005457 optimization Methods 0.000 title claims abstract description 30
- 238000000034 method Methods 0.000 title claims abstract description 20
- 230000005540 biological transmission Effects 0.000 claims description 3
- 238000012913 prioritisation Methods 0.000 description 6
- 238000004364 calculation method Methods 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 1
- 238000000205 computational method Methods 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000006467 substitution reaction Methods 0.000 description 1
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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Abstract
The invention provides a kind of centre-to-centre spacing optimization method, gearbox and the vehicle of parallel axes system.Method includes：S1, the centre-to-centre spacing AD of centre-to-centre spacing BC, the centre-to-centre spacing CD of the second counter drive shaft and output shaft, the first counter drive shaft and the output shaft of centre-to-centre spacing AB, input shaft and the second counter drive shaft of the first counter drive shaft and input shaft is determined, XY coordinate systems are set up by origin of the axle center of input shaft on the vertical plane of parallel axes system；S2, first counter drive shaft, input shaft, the second counter drive shaft, output shaft are corresponding in turn to coordinate points A (Xa in XY coordinate systems, Ya), B (Xb, Yb), C (Xc, Yc), D (Xd, Yd), obtains one according to the connection order of parallel axes system and optimizes constraints；S3, determines that an object function F (x) obtains an at least extreme value so that the centre-to-centre spacing BD minimum values of input shaft and output shaft, obtain BD, α 1, the α 2 when BD is minimum value under optimization constraints.BD, α 1, α 2 when S4 is minimum value according to the BD obtain A (Xa, Ya), C (Xc, Yc), D (Xd, Yd) optimization coordinate.
Description
Technical field
The present invention relates to parallel axes technical field, in particular it relates to a kind of centre-to-centre spacing optimization method of parallel axes system, change
Fast case and vehicle.
Background technology
Centre-to-centre spacing refers to the beeline between gear pair with parallel axes or gear pair with non-parallel, two axial lines, that is, two gear shafts
Common vertical line (line of centres) length claims gear centre away from abbreviation centre-to-centre spacing between line.Its value is always equal to the pitch radius sum of gear pair two,
Or equal to two reference radius and fractional dose sum.As the determination of the centre-to-centre spacing at different levels in 2AT parallel axes systems, it is different in
The heart can then cause different speed changer profiles away from arrangement, and traditional design method mainly determines input shaft according to personal experience
With the distance of output shaft, it can not determine whether the distance of input shaft and output shaft has reached minimum completely, if also have time
Between diminish, so as to not can confirm that under existence conditions whether gearbox is to optimize, so as to easily become large-sized gearbox,
Structure is not compact, increases the cost of gearbox.
The content of the invention
For defect of the prior art, it is an object of the invention to provide a kind of centre-to-centre spacing optimization side of parallel axes system
Method, gearbox and vehicle.
A kind of centre-to-centre spacing optimization method of the parallel axes system provided according to the present invention, parallel axes system includes the first secondary biography
Moving axis, input shaft, the second counter drive shaft, output shaft, including：
S1, is determined according to the radius that gear is arranged on the first counter drive shaft, input shaft, the second counter drive shaft, output shaft
The centre-to-centre spacing BC of the centre-to-centre spacing AB of one counter drive shaft and input shaft, input shaft and the second counter drive shaft, the second counter drive shaft with it is defeated
The centre-to-centre spacing CD of shaft, the first counter drive shaft and output shaft centre-to-centre spacing AD, with input shaft on the vertical plane of parallel axes system
Axle center set up XY coordinate systems for origin；
S2, first counter drive shaft, input shaft, the second counter drive shaft, output shaft are right successively in the XY coordinate systems
Coordinate points A (Xa, Ya), B (Xb, Yb), C (Xc, Yc), D (Xd, Yd) are answered, it is excellent to obtain one according to the connection order of parallel axes system
Changing constraints includes：
(Xd-Xc) ^2+ (Yd-Yc) ^2=CD^2,
(Xd-Xa) ^2+ (Yd-Ya) ^2=AD^2,
0 ° of 45 ° of 1 ＜ of ＜ α, 150 ° of 180 ° of 2 ＜ of ＜ α,
Xa=AB*cos (α 2), Ya=AB*sin (α 2), Xc=BC*cos (180- α 1), Yc=BC*sin (180- α 1),
Wherein, the α 1 is the second counter drive shaft and the angle of X-coordinate axle, and the α 2 is the first counter drive shaft and X-coordinate
The angle of axle；
S3, determines that an object function F (x) obtains an at least extreme value so that the input shaft under the optimization constraints
With the centre-to-centre spacing BD minimum values of output shaft, BD, α 1, the α 2 when the BD is minimum value are obtained；
S4, BD, α 1, α 2 during according to the BD for minimum value obtain A (Xa, Ya), C (Xc, Yc), D (Xd, Yd) optimization
Coordinate.
As a kind of prioritization scheme, object function F (x)=Xd^2+Yd^2 in the S3.
Based on same inventive concept, present invention also offers a kind of gearbox, including by putting down that the optimization method is determined
Row axle system.
As a kind of prioritization scheme, the input shaft drives first counter drive shaft, second by travelling gear respectively
Counter drive shaft is rotated, and first counter drive shaft, the second counter drive shaft also drive the output shaft rotation respectively.
As a kind of prioritization scheme, the first travelling gear, the first drive gear, are provided with first counter drive shaft
One clutch；First travelling gear is placed on first counter drive shaft, first drive gear and described first
Counter drive shaft is fixedly and coaxially connected, and first travelling gear connects first drive gear by the first clutch,
The input shaft connects first counter drive shaft by first travelling gear, and first counter drive shaft passes through described the
One drive gear connects the output shaft.
As a kind of prioritization scheme, the second travelling gear, the second drive gear, are provided with second counter drive shaft
Two clutches；Second travelling gear is placed on second counter drive shaft, second drive gear and described second
Counter drive shaft is fixedly and coaxially connected, and second travelling gear connects second drive gear by the second clutch,
The input shaft connects second counter drive shaft by second travelling gear, and second counter drive shaft passes through described the
Two drive gears connect the output shaft.
As a kind of prioritization scheme, the radius of first travelling gear is less than the radius of second travelling gear；Institute
The radius for stating the first drive gear is less than the radius of second drive gear.
As a kind of prioritization scheme, the radius of first travelling gear is more than the radius of first drive gear；Institute
The radius for stating the second travelling gear is more than the radius of second drive gear.
Based on same inventive concept, the invention provides a kind of vehicle, including described gearbox.
Compared with prior art, the present invention has following beneficial effect：
By input and output centre-to-centre spacing in structure optimization constraints and the method acquisition parallel axes system of object function most
Small value, and then obtain the minimum dimension of whole parallel axes system so that overall system structure is compact, reduces cost.
Brief description of the drawings
In order to illustrate the technical solution of the embodiments of the present invention more clearly, being used required in being described below to embodiment
Accompanying drawing be briefly described, it is therefore apparent that drawings in the following description are only some embodiments of the present invention, for ability
For field technique personnel, on the premise of not paying creative work, other accompanying drawings can also be obtained according to these accompanying drawings.It is attached
In figure：
Fig. 1 is a kind of optional parallel axes system structure diagram；
Fig. 2 is a kind of optional XY coordinates set up on the vertical plane of parallel axes system by origin of the axle center of input shaft
It is schematic diagram；
Fig. 3 is a kind of centre-to-centre spacing optimization method schematic flow sheet of optional parallel axes system.
Embodiment
Below in conjunction with accompanying drawing, the present invention is described in detail in the way of specific embodiment.Following examples will be helpful to
Those skilled in the art further understands the present invention, but the invention is not limited in any way.It should be pointed out that can be with
Using other embodiments, or modification structurally and functionally is carried out to embodiment enumerated herein, without departing from this hair
Bright scope and spirit.
In a kind of embodiment of the centre-to-centre spacing optimization method for parallel axes system that the present invention is provided, parallel axes system includes
First counter drive shaft, input shaft, the second counter drive shaft, output shaft, method flow as shown in Figure 3 include：
S1, is determined according to the radius that gear is arranged on the first counter drive shaft, input shaft, the second counter drive shaft, output shaft
The centre-to-centre spacing BC of the centre-to-centre spacing AB of one counter drive shaft and input shaft, input shaft and the second counter drive shaft, the second counter drive shaft with it is defeated
The centre-to-centre spacing CD of shaft, the first counter drive shaft and output shaft centre-to-centre spacing AD, with input shaft on the vertical plane of parallel axes system
Axle center set up XY coordinate systems for origin.Because optimization object is parallel axes system, therefore each rotating shaft drift angle in Z-direction is all 0,
Without considering.
The a kind of optional of the specific method of centre-to-centre spacing between two axles is determined according to the radius that gear is arranged on axle in step S1
Embodiment includes root radius R1, the R2 for determining to engage the gear being arranged on two axles of connection by gear, and mutually nibbles
The fully teeth height h (radial distance between outside circle and root circle) of one of two gears closed, centre-to-centre spacing=R1+R2+h.The calculating
Mode consider to be meshed position gear it is overlapping, and engagement place is the most short position of two gears distance, be between two axles most
Short distance.
S2, as shown in Figure 1, 2, first counter drive shaft, input shaft, the second counter drive shaft, output shaft are sat in the XY
Coordinate points A (Xa, Ya), B (Xb, Yb), C (Xc, Yc), D (Xd, Yd), according to the connection of parallel axes system are corresponding in turn in mark system
Order, which obtains an optimization constraints, to be included：
(Xd-Xc) ^2+ (Yd-Yc) ^2=CD^2,
(Xd-Xa) ^2+ (Yd-Ya) ^2=AD^2,
0 ° of 45 ° of 1 ＜ of ＜ α, 150 ° of 180 ° of 2 ＜ of ＜ α,
Xa=AB*cos (α 2), Ya=AB*sin (α 2), Xc=BC*cos (180- α 1), Yc=BC*sin (180- α 1),
Wherein, the α 1 is the second counter drive shaft and the angle of X-coordinate axle, and the α 2 is the first counter drive shaft and X-coordinate
The angle of axle.
First counter drive shaft described in step S2, input shaft, the second counter drive shaft, the vertical plane of output shaft and parallel axes system
It is respectively present and only exists an intersection point, the intersection point is also the point that hangs down.As shown in Fig. 2 first counter drive shaft and parallel axis system
The intersection point of the vertical plane of system respective coordinates point A (Xa, Ya) in a coordinate system；The input shaft and the vertical plane of parallel axes system
Intersection point respective coordinates point B (Xb, Yb) in a coordinate system, B points are also the origin of coordinates (0,0)；Second counter drive shaft with it is parallel
The intersection point of the vertical plane of axle system respective coordinates point C (Xc, Yc) in a coordinate system；The output shaft is vertical with parallel axes system
The intersection point in face respective coordinates point D (Xd, Yd) in a coordinate system.Centre-to-centre spacing AB, BC, CD, AD are, it is known that input shaft central point B is seat
Origin is marked, secondary drive shaft is unknown with the angle α 2 of trunnion axis, and three-level power transmission shaft is unknown with the angle α 1 of trunnion axis, the mesh of optimization
It is designated as asking for minimum range of the input shaft center with output shaft center.
The coordinate value of each axle in a coordinate system can be represented by down in parallel axes system：
By above-mentioned optimization constraints can in the hope of the coordinate Xd, Yd of D points expression formula, unknown α is included in expression formula
1、α2。
S3, determines that an object function F (x) obtains an at least extreme value so that the input shaft under the optimization constraints
With the centre-to-centre spacing BD minimum values of output shaft, BD, α 1, the α 2 when the BD is minimum value are obtained.
S4, BD, α 1, α 2 during according to the BD for minimum value obtain A (Xa, Ya), C (Xc, Yc), D (Xd, Yd) optimization
Coordinate.The positioning of each rotating shaft of parallel axes system is this completes, obtains cause centre-to-centre spacing between input and output shaft minimum
Optimize structure.
As a kind of embodiment, the distance with D points relative to B points, i.e. centre-to-centre spacing BD are used as object function F (x)=(Xd-
Xb) ^2+ (Yd-Yb) ^2, and because B points are the origin of coordinates, therefore Xb=0, Yb=0, that is, being converted into solution has object function F
(x)=Xd^2+Yd^2 minimum value.
Obtained according to equation after minimum value, in the case where considering that the other parts such as bearing are not interfered, in i.e. fixed
The heart is obtained after input shaft and output shaft minimum value according to above-mentioned computational methods, suitably adjusted with reference to actual conditions away from numerical value
Optimum center distance and structure arrangement are obtained, so as to save space, cost is reduced.
Calculated and obtained according to above-mentioned optimization constraintsWith reference to Xa=AB*cos
(α 2), Ya=AB*sin (α 2), Xc=BC*cos (180- α 1), Yc=BC*sin (180- α 1) obtains the calculation expression on Yd
Formula：(BC*COS (180- α 1)-AB*COS α 2) ^2=AD^2+CD^2- (Yd-AB*SIN α 2) ^2- (Yd-BC*SIN (180- α 1))
^2±2*SQRT((AD^2-(Yd-AB*SINα2)^2)*(CD^2-(Yd-BC*SIN(180-α1))^2)；
Calculated and obtained according to above-mentioned optimization constraintsWith reference to Xa=AB*cos
(α 2), Ya=AB*sin (α 2), Xc=BC*cos (180- α 1), Yc=BC*sin (180- α 1) obtains the calculation expression on Xd
Formula：(BC*SIN (180- α 1)-AB*SIN α 2) ^2=D^2+AD^2- (Xd-BC*COS (180- α 1)) ^2- (Xd-AB*COS α 2) ^
2±2*SQRT((CD^2-(Xd-BC*COS(180-α1))^2-(AD^2-(Xd-AB*COSα2))^2)。
Object function F (x)=Xd^2+Yd^2 track is ellipse, because object function is ellipse, therefore in order to take
To rational monodrome as a result, it is desirable to constrain angle, i.e. constraints：0 ° of 1 ＜ of ＜ α, 45 ° of 180 ° of 150 ° of ＜ α, 2 ＜.
α 1 and α 2 are found in a coordinate system so that F (x) minimum value, thereby determines that Xd and Yd value.
Based on same inventive concept, present invention also offers a kind of gearbox, including by putting down that the optimization method is determined
Row axle system.
The input shaft drives first counter drive shaft, the second counter drive shaft to rotate respectively by travelling gear, described
First counter drive shaft, the second counter drive shaft also drive the output shaft rotation respectively.
The first travelling gear, the first drive gear, first clutch are provided with first counter drive shaft；Described first
Travelling gear is placed on first counter drive shaft, and coaxially fixation connects first drive gear with first counter drive shaft
Connect, first travelling gear connects first drive gear by the first clutch, and the input shaft passes through described
First travelling gear connects first counter drive shaft, and first counter drive shaft connects described by first drive gear
Output shaft.
The second travelling gear, the second drive gear, second clutch are provided with second counter drive shaft；Described second
Travelling gear is placed on second counter drive shaft, and coaxially fixation connects second drive gear with second counter drive shaft
Connect, second travelling gear connects second drive gear by the second clutch, and the input shaft passes through described
Second travelling gear connects second counter drive shaft, and second counter drive shaft connects described by second drive gear
Output shaft.
The radius of first travelling gear is less than the radius of second travelling gear；The half of first drive gear
Footpath is less than the radius of second drive gear.
The radius of first travelling gear is more than the radius of first drive gear；The half of second travelling gear
Footpath is more than the radius of second drive gear.
Based on same inventive concept, present invention also offers a kind of vehicle, including described gearbox.Above-mentioned gearbox energy
Minimum dimension is enough obtained by optimization method, whole parallel axes system internal structure is compact, reduces the holistic cost of gearbox.
Presently preferred embodiments of the present invention is the foregoing is only, those skilled in the art know, do not departing from the essence of the present invention
In the case of refreshing and scope, various changes or equivalent substitution can be carried out to these features and embodiment.In addition, the present invention's
Under teaching, these features and embodiment can be modified to adapt to particular situation and material without departing from the present invention's
Spirit and scope.Therefore, the present invention is not limited to the particular embodiment disclosed, and the right for falling with the application will
Embodiment in the range of asking belongs to protection scope of the present invention.
Claims (9)
1. a kind of centre-to-centre spacing optimization method of parallel axes system, parallel axes system includes the first counter drive shaft, input shaft, the second pair
Power transmission shaft, output shaft, it is characterised in that including：
S1, determines that first is secondary according to the radius that gear is arranged on the first counter drive shaft, input shaft, the second counter drive shaft, output shaft
Centre-to-centre spacing AB, the centre-to-centre spacing BC of input shaft and the second counter drive shaft, the second counter drive shaft and the output shaft of power transmission shaft and input shaft
Centre-to-centre spacing CD, the centre-to-centre spacing AD of the first counter drive shaft and output shaft, with the axle of input shaft on the vertical plane of parallel axes system
The heart is that origin sets up XY coordinate systems；
S2, first counter drive shaft, input shaft, the second counter drive shaft, output shaft are corresponding in turn to seat in the XY coordinate systems
Punctuate A (Xa, Ya), B (Xb, Yb), C (Xc, Yc), D (Xd, Yd), an optimization is obtained about according to the connection order of parallel axes system
Beam condition includes：
(Xd-Xc) ^2+ (Yd-Yc) ^2=CD^2,
(Xd-Xa) ^2+ (Yd-Ya) ^2=AD^2,
0°<α1<45 °, 150 °<α2<180 °,
Xa=AB*cos (α 2), Ya=AB*sin (α 2), Xc=BC*cos (180- α 1), Yc=BC*sin (180- α 1),
Wherein, the α 1 is the second counter drive shaft and the angle of X-coordinate axle, and the α 2 is the first counter drive shaft and X-coordinate axle
Angle；
S3, determine an object function F (x) it is described optimization constraints under obtain an at least extreme value so that the input shaft with it is defeated
The centre-to-centre spacing BD minimum values of shaft, obtain BD, α 1, the α 2 when the BD is minimum value；
S4, BD, α 1, α 2 during according to the BD for minimum value obtain A (Xa, Ya), and C (Xc, Yc), D (Xd, Yd) optimization is sat
Mark.
2. a kind of centre-to-centre spacing optimization method of parallel axes system according to claim 1, it is characterised in that mesh in the S3
Scalar functions F (x)=Xd^2+Yd^2.
3. a kind of gearbox, it is characterised in that including the parallel axis system determined by any optimization methods of claim 1-3
System.
4. a kind of gearbox according to claim 3, it is characterised in that the input shaft is driven respectively by travelling gear
First counter drive shaft, the second counter drive shaft are rotated, and first counter drive shaft, the second counter drive shaft also drive described respectively
Output shaft rotation.
5. a kind of gearbox according to claim 4, it is characterised in that be provided with the first biography on first counter drive shaft
Moving gear, the first drive gear, first clutch；First travelling gear is placed on first counter drive shaft, described
First drive gear is fixedly and coaxially connected with first counter drive shaft, and first travelling gear passes through the first clutch
First drive gear is connected, the input shaft connects first counter drive shaft by first travelling gear, described
First counter drive shaft connects the output shaft by first drive gear.
6. a kind of gearbox according to claim 5, it is characterised in that be provided with the second biography on second counter drive shaft
Moving gear, the second drive gear, second clutch；Second travelling gear is placed on second counter drive shaft, described
Second drive gear is fixedly and coaxially connected with second counter drive shaft, and second travelling gear passes through the second clutch
Second drive gear is connected, the input shaft connects second counter drive shaft by second travelling gear, described
Second counter drive shaft connects the output shaft by second drive gear.
7. a kind of gearbox according to claim 6, it is characterised in that the radius of first travelling gear is less than described
The radius of second travelling gear；The radius of first drive gear is less than the radius of second drive gear.
8. a kind of gearbox according to claim 6, it is characterised in that the radius of first travelling gear is more than described
The radius of first drive gear；The radius of second travelling gear is more than the radius of second drive gear.
9. a kind of vehicle, it is characterised in that including gearbox as claimed in claim 3.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710237541.XA CN107061639B (en) | 2017-04-12 | 2017-04-12 | A kind of center of parallel axes system is away from optimization method, gearbox and vehicle |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710237541.XA CN107061639B (en) | 2017-04-12 | 2017-04-12 | A kind of center of parallel axes system is away from optimization method, gearbox and vehicle |
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| Publication Number | Publication Date |
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| CN107061639A true CN107061639A (en) | 2017-08-18 |
| CN107061639B CN107061639B (en) | 2019-06-11 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN201710237541.XA Expired - Fee Related CN107061639B (en) | 2017-04-12 | 2017-04-12 | A kind of center of parallel axes system is away from optimization method, gearbox and vehicle |
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Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1813145A (en) * | 2003-07-04 | 2006-08-02 | 腓特烈斯港齿轮工厂股份公司 | Powershift gearbox for construction machines, especially for a tractor backhoe loader and a telescopic handler |
| CN202392055U (en) * | 2011-11-09 | 2012-08-22 | 广西柳工机械股份有限公司 | Hydraulic mechanical gear box of engineering machinery |
| CN202561013U (en) * | 2012-04-23 | 2012-11-28 | 无锡天野数控装备有限公司 | Inter-shaft center distance adjustment mechanism |
| KR101475858B1 (en) * | 2014-07-11 | 2014-12-23 | 경종우 | A speed variable transmission using a roller |
| CN104834790A (en) * | 2015-05-22 | 2015-08-12 | 南通中远船务工程有限公司 | Tolerance analysis method for space dimension chain |
| JP5837471B2 (en) * | 2012-10-02 | 2015-12-24 | 日立建機株式会社 | Power transmission device for vehicle |
-
2017
- 2017-04-12 CN CN201710237541.XA patent/CN107061639B/en not_active Expired - Fee Related
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1813145A (en) * | 2003-07-04 | 2006-08-02 | 腓特烈斯港齿轮工厂股份公司 | Powershift gearbox for construction machines, especially for a tractor backhoe loader and a telescopic handler |
| CN202392055U (en) * | 2011-11-09 | 2012-08-22 | 广西柳工机械股份有限公司 | Hydraulic mechanical gear box of engineering machinery |
| CN202561013U (en) * | 2012-04-23 | 2012-11-28 | 无锡天野数控装备有限公司 | Inter-shaft center distance adjustment mechanism |
| JP5837471B2 (en) * | 2012-10-02 | 2015-12-24 | 日立建機株式会社 | Power transmission device for vehicle |
| KR101475858B1 (en) * | 2014-07-11 | 2014-12-23 | 경종우 | A speed variable transmission using a roller |
| CN104834790A (en) * | 2015-05-22 | 2015-08-12 | 南通中远船务工程有限公司 | Tolerance analysis method for space dimension chain |
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| Publication number | Publication date |
|---|---|
| CN107061639B (en) | 2019-06-11 |
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