CN111746302B - Commercial vehicle transmission shaft matching method - Google Patents
Commercial vehicle transmission shaft matching method Download PDFInfo
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- CN111746302B CN111746302B CN202010652396.3A CN202010652396A CN111746302B CN 111746302 B CN111746302 B CN 111746302B CN 202010652396 A CN202010652396 A CN 202010652396A CN 111746302 B CN111746302 B CN 111746302B
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- transmission shaft
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Classifications
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60L—PROPULSION OF ELECTRICALLY-PROPELLED VEHICLES; SUPPLYING ELECTRIC POWER FOR AUXILIARY EQUIPMENT OF ELECTRICALLY-PROPELLED VEHICLES; ELECTRODYNAMIC BRAKE SYSTEMS FOR VEHICLES IN GENERAL; MAGNETIC SUSPENSION OR LEVITATION FOR VEHICLES; MONITORING OPERATING VARIABLES OF ELECTRICALLY-PROPELLED VEHICLES; ELECTRIC SAFETY DEVICES FOR ELECTRICALLY-PROPELLED VEHICLES
- B60L15/00—Methods, circuits, or devices for controlling the traction-motor speed of electrically-propelled vehicles
- B60L15/20—Methods, circuits, or devices for controlling the traction-motor speed of electrically-propelled vehicles for control of the vehicle or its driving motor to achieve a desired performance, e.g. speed, torque, programmed variation of speed
- B60L15/2054—Methods, circuits, or devices for controlling the traction-motor speed of electrically-propelled vehicles for control of the vehicle or its driving motor to achieve a desired performance, e.g. speed, torque, programmed variation of speed by controlling transmissions or clutches
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60L—PROPULSION OF ELECTRICALLY-PROPELLED VEHICLES; SUPPLYING ELECTRIC POWER FOR AUXILIARY EQUIPMENT OF ELECTRICALLY-PROPELLED VEHICLES; ELECTRODYNAMIC BRAKE SYSTEMS FOR VEHICLES IN GENERAL; MAGNETIC SUSPENSION OR LEVITATION FOR VEHICLES; MONITORING OPERATING VARIABLES OF ELECTRICALLY-PROPELLED VEHICLES; ELECTRIC SAFETY DEVICES FOR ELECTRICALLY-PROPELLED VEHICLES
- B60L2240/00—Control parameters of input or output; Target parameters
- B60L2240/40—Drive Train control parameters
- B60L2240/48—Drive Train control parameters related to transmissions
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/60—Other road transportation technologies with climate change mitigation effect
- Y02T10/72—Electric energy management in electromobility
Abstract
The invention discloses a method for matching transmission shafts of commercial vehicles, and belongs to the technical field of transmission shaft matching. The commercial vehicle transmission shaft matching method comprises the following steps: s1: a transmission shaft conforming to the transmission and the rear bridging disc is selected by the transmission and the rear bridging disc; s2: calculating a maximum torque T of a vehicle comprising the transmission and the rear bridging disc max The method comprises the steps of carrying out a first treatment on the surface of the S3: calculating the excess coefficient n of the transmission shaft e And select n e A drive shaft of < 1.5; s4: calculating the critical rotation speed n of the transmission shaft k The method comprises the steps of carrying out a first treatment on the surface of the S5: calculating the actual maximum rotation speed n of the transmission shaft s Theoretical maximum rotational speed n of the drive shaft f And the allowable maximum rotational speed n of the transmission shaft max The following requirements are satisfied: n is n s ＜n max And n is f ＜n max The transmission shaft is a transmission shaft which is qualified in matching. The specification of the transmission shaft matched by the method is smaller than that of the transmission shaft obtained by the prior art, the cost of the transmission shaft can be greatly reduced, and meanwhile, the reliability of the transmission shaft can be effectively improved.
Description
Technical Field
The invention relates to the technical field of transmission shafts, in particular to a matching method for a transmission shaft of a commercial vehicle.
Background
In the prior art, the transmission shaft of the commercial vehicle needs to be designed and matched except considering the boundary condition of the transmission shaft, and the existing matching method mainly considers two aspects, namely torque matching, maximum output torque of a required vehicle type is smaller than rated torque of the transmission shaft, critical rotation speed matching, maximum rotation speed is required to be smaller than critical rotation speed of the transmission shaft, and the rotation speed of an engine at maximum output power is generally adopted when the maximum rotation speed is calculated.
The matching method in the prior art has the problems that for torque matching, the actual use torque of the commercial vehicle is not larger than the maximum torque of the vehicle type in the actual use process, the maximum output torque of the vehicle type is required to be achieved, the engine is required to be in the maximum output torque state, the load is required to reach the maximum weight borne by the vehicle type, namely under the serious overload condition, and the road condition is in an extreme state, so that the probability of occurrence of the probability is small in the actual use, the performance of the matched transmission shaft is too high when the transmission shaft is matched, the cost of the transmission shaft is greatly increased, and the matching method is very uneconomical for manufacturers and users.
On the other hand, for critical rotation speed, in the actual use process, the maximum rotation speed of the engine is very unsuitable to match, because when the user runs down a slope, individual users use neutral sliding for saving oil, the rotation speed of the engine is not high, but the rotation speed of the vehicle is far greater than the rotation speed obtained by forward calculation of the vehicle, so that the rotation speed of the vehicle is too high, especially when the rotation speed is greater than the critical rotation speed in the process of running down an empty vehicle, the transmission shaft is caused to shake together, so that the transmission shaft is damaged and broken, and serious accidents such as vehicle rollover are caused.
Disclosure of Invention
The invention aims to provide a commercial vehicle transmission shaft matching method, which aims to solve the technical problems in the background technology, namely, the cost of the transmission shaft of a vehicle is effectively reduced, and the use safety of the transmission shaft is improved.
In order to achieve the above purpose, the present invention adopts the following technical scheme:
a method of commercial vehicle drive shaft mating comprising:
s1: a transmission shaft conforming to the transmission and the rear bridging disc is selected by the transmission and the rear bridging disc;
s2: calculating a maximum torque T of a vehicle comprising the transmission and the rear bridging disc max ；
S3: calculating the excess coefficient n of the transmission shaft e And select n e A drive shaft of < 1.5;
s4: calculating the critical rotation speed n of the transmission shaft k ；
S5: calculating the actual maximum rotation speed n of the transmission shaft s Theoretical maximum rotational speed n of the drive shaft f And the allowable maximum rotational speed n of the transmission shaft max The following requirements are satisfied: n is n s ＜n max And n is f ＜n max The transmission shaft is a transmission shaft which is qualified in matching.
Further, in S2, maximum torque T max The determination method of (1) is as follows: by taking the forward torque sum of the vehicleMaximum reverse torque as maximum torque T of the vehicle max ，
The said
The said
Wherein: t: engine output maximum torque (NM);
i max : the highest speed ratio of the transmission;
η: transmission efficiency of a transmission
K d : dynamic load coefficient;
n: the number of drive axles;
g: maximum load (kg);
m is the rear axle load transfer coefficient when the automobile is at maximum acceleration;
r is the tire rolling radius (m);
phi: adhesion coefficient between the tire and the road surface;
etam is the transmission efficiency between the main reducer driving gear and the wheels;
i 0 : a main reduction ratio;
i m : the final drive is driven by the gear ratio to the vehicle.
In the embodiment, in S3, the excess coefficient n of the transmission shaft e The calculation method of (2) is as follows:
wherein T is Forehead (forehead) : rated torque of the transmission shaft.
Optionally, in S4, the critical rotation speed n of the transmission shaft k The calculation method of (2) is as follows:
wherein: d: shaft tube outer diameter (mm) of the drive shaft;
d: the inner diameter (mm) of the shaft tube of the transmission shaft;
l: the length dimension (mm) between two gimbals.
Further, in S5, the n f 、n s 、n max The calculation method of (2) is as follows:
n s ＝n×i min ；
n max ＝0.67×n k ；
wherein, the liquid crystal display device comprises a liquid crystal display device,
n is the highest rotation speed (r/min) of the engine;
v: vehicle maximum speed (km/h);
i min the lowest speed ratio of the transmission.
Further, in S5, if n s ≥n max And/or n f ≥n max The critical rotation speed n of the transmission shaft is increased by increasing the outer diameter D of the shaft tube of the transmission shaft k 。
Further, the saidIn the above, the value of v is 120km/h.
Further, when the matching result has a plurality of qualified transmission shafts, the excess coefficient n of the transmission shafts is selected e A drive shaft closest to 1.5.
Compared with the prior art, the invention has the following beneficial effects:
the specification of the transmission shaft matched by the method is smaller than that of the transmission shaft obtained by the prior art, and the cost of the transmission shaft can be greatly reduced (the main cost is on the cross shaft of the universal joint), so that the cost of the assembly of the transmission shaft can be greatly reduced on the basis of the prior art by the matching, and the reliability of the transmission shaft can be effectively improved.
Detailed Description
The present invention is further described below in conjunction with embodiments, which are merely some, but not all embodiments of the present invention. Based on the embodiments of the present invention, other embodiments that may be used by those of ordinary skill in the art without making any inventive effort are within the scope of the present invention.
Example 1:
a method of commercial vehicle drive shaft mating comprising:
step S1: a transmission shaft conforming to the transmission and the rear bridging disc is selected by the transmission and the rear bridging disc;
step S2: calculating a maximum torque T of a vehicle comprising the transmission and the rear bridging disc max ；
In S2, maximum torque T max The determination method of (1) is as follows: by taking the maximum of the forward torque and the reverse torque of the vehicle as the maximum torque T of the vehicle max ，
The T is Positive direction ＝T×i max ，
The said
Wherein: i.e max : the transmission highest gear ratio;
t: maximum torque of the engine;
g: maximum load (kg);
r: the rolling radius (m) of the tyre;
k: road surface adhesion coefficient;
f p : load transfer coefficient.
Step S3: calculating the excess coefficient n of the transmission shaft e And select n e A drive shaft of < 1.5;
in S3, the excess coefficient n of the transmission shaft e The calculation method of (2) is as follows:
wherein T is Forehead (forehead) : rated torque of the transmission shaft.
Step S4: calculating the critical rotation speed n of the transmission shaft k ；
In S4, critical rotation speed n of the transmission shaft k The calculation method of (2) is as follows:
wherein: d: shaft tube outer diameter (mm) of the drive shaft;
d: the inner diameter (mm) of the shaft tube of the transmission shaft;
l: the length dimension (mm) between two gimbals.
Step S5: calculating the actual maximum rotation speed n of the transmission shaft s Theoretical maximum rotational speed n of the drive shaft f And the allowable maximum rotational speed n of the transmission shaft max The following requirements are satisfied: n is n s ＜n max And n is f ＜n max The transmission shaft is a transmission shaft which is qualified in matching.
In the S5, the n f 、n s 、n max The calculation method of (2) is as follows:
n s ＝n×i min ；
n max ＝0.67×n k ；
wherein, the liquid crystal display device comprises a liquid crystal display device,
n is the highest rotation speed (r/min) of the engine;
v: vehicle maximum speed (km/h);
i min the lowest speed ratio of the speed changer;
i 0 : a main reduction ratio;
r is the tire rolling radius (m);
i m : the final drive is driven by the gear ratio to the vehicle.
Wherein in S5, if n s ≥n max And/or n f ≥n max The critical rotation speed n of the transmission shaft is increased by increasing the outer diameter D of the shaft tube of the transmission shaft k 。
Preferably, the saidIn the above, the value of v is 120km/h.
In the technical scheme of the invention, when the vehicle speed is calculated, the fixed speed per hour is adopted for calculation, the V=120 km/h is usually adopted for calculation, the calculation is not carried out through the rotation speed of an engine, the value obtained through the calculation is usually between 60km/h and 90km/h, and is far less than 120km/h, so that the obtained theoretical maximum practical rotation speed is greatly improved, and the vehicle is reliable when actually driven below the speed.
The specification of the transmission shaft obtained by the excess coefficient is smaller than that of the transmission shaft obtained by the prior art, and the cost of the transmission shaft can be greatly reduced (the main cost is on the cross shaft of the universal joint); when the matching result has a plurality of qualified transmission shafts, selecting the excess coefficient n of the transmission shafts e A drive shaft closest to 1.5.
Therefore, through the matching, the assembly cost of the transmission shaft can be greatly reduced on the basis of the prior art, and meanwhile, the reliability of the transmission shaft can be effectively improved.
The foregoing description of the preferred embodiments of the invention is not intended to be limiting, but rather is intended to cover all modifications, equivalents, and alternatives falling within the spirit and principles of the invention.
Claims (2)
1. A method for matching a drive shaft of a commercial vehicle, comprising:
s1: a transmission shaft conforming to the transmission and the rear bridging disc is selected by the transmission and the rear bridging disc;
s2: calculating a maximum torque T of a vehicle comprising the transmission and the rear bridging disc max ；
S3: calculating the excess coefficient n of the transmission shaft e And select n e A drive shaft of < 1.5;
s4: calculating the critical rotation speed n of the transmission shaft k ；
S5: calculating the actual maximum rotation speed n of the transmission shaft s Theoretical maximum rotational speed n of the drive shaft f And the allowable maximum rotational speed n of the transmission shaft max The following requirements are satisfied: n is n s ＜n max And n is f ＜n max The transmission shaft is a transmission shaft which is qualified in matching;
in S2, maximum torque T max The determination method of (1) is as follows: by taking the maximum of the forward torque and the reverse torque of the vehicle as the maximum torque T of the vehicle max ，
The said
The said
Wherein: t: engine output maximum torque (NM);
i max : the highest speed ratio of the transmission;
η: transmission efficiency of a transmission
K d : dynamic load coefficient;
n: the number of drive axles;
g: maximum load (kg);
m is the rear axle load transfer coefficient when the automobile is at maximum acceleration;
r is the tire rolling radius (m);
phi: adhesion coefficient between the tire and the road surface;
etam is the transmission efficiency between the main reducer driving gear and the wheels;
i 0 : a main reduction ratio;
i m : a ratio of the final drive driven gear to the vehicle;
in S3, the excess coefficient n of the transmission shaft e The calculation method of (2) is as follows:
wherein T is Forehead (forehead) : rated torque of the transmission shaft;
in S4, critical rotation speed n of the transmission shaft k The calculation method of (2) is as follows:
wherein: d: shaft tube outer diameter (mm) of the drive shaft;
d: the inner diameter (mm) of the shaft tube of the transmission shaft;
l: a length dimension (mm) between two gimbals;
in the S5, the n f 、n s 、n max The calculation method of (2) is as follows:
n s ＝n×i min ；
n max ＝0.67×n k ；
wherein, the liquid crystal display device comprises a liquid crystal display device,
n is the highest rotation speed (r/min) of the engine;
v: vehicle maximum speed (km/h);
i min the lowest speed ratio of the speed changer;
i 0 : a main reduction ratio;
r is the tire rolling radius (m);
i m : final drive driven gear to vehicleA transmission ratio between;
the saidIn the method, the value of v is 120km/h;
in S5, when the matching result has a plurality of qualified transmission shafts, selecting excess coefficient n of the transmission shafts e A drive shaft closest to 1.5.
2. The method for matching a transmission shaft of a commercial vehicle according to claim 1, wherein in S5, if n s ≥n max And/or n f ≥n max The critical rotation speed n of the transmission shaft is increased by increasing the outer diameter D of the shaft tube of the transmission shaft k 。
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202010652396.3A CN111746302B (en) | 2020-07-08 | 2020-07-08 | Commercial vehicle transmission shaft matching method |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202010652396.3A CN111746302B (en) | 2020-07-08 | 2020-07-08 | Commercial vehicle transmission shaft matching method |
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| Publication Number | Publication Date |
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| CN111746302A CN111746302A (en) | 2020-10-09 |
| CN111746302B true CN111746302B (en) | 2023-07-18 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN202010652396.3A Active CN111746302B (en) | 2020-07-08 | 2020-07-08 | Commercial vehicle transmission shaft matching method |
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Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102338193A (en) * | 2010-07-16 | 2012-02-01 | 中国第一汽车集团公司 | Transmission shaft |
| CN106523512A (en) * | 2016-12-15 | 2017-03-22 | 安徽天瑞精密汽车零部件有限公司 | Novel forklift pump drive shaft |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102007021733B4 (en) * | 2007-05-09 | 2011-03-10 | Agco Gmbh | Drive arrangement for vehicles with at least two drivable vehicle axles |
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2020
- 2020-07-08 CN CN202010652396.3A patent/CN111746302B/en active Active
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102338193A (en) * | 2010-07-16 | 2012-02-01 | 中国第一汽车集团公司 | Transmission shaft |
| CN106523512A (en) * | 2016-12-15 | 2017-03-22 | 安徽天瑞精密汽车零部件有限公司 | Novel forklift pump drive shaft |
Non-Patent Citations (2)
| Title |
|---|
| 佟杰.浅谈某轻卡车型的传动轴匹配设计.汽车实用技术.2017,2017年(第18期),第66-68页. * |
| 苗学刚.发动机试验台架弹性传动轴设计与匹配研究.现代车用动力.2018,2018年(第3期),第21-24页. * |
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| CN111746302A (en) | 2020-10-09 |
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