CN113449405A - Heavy commercial vehicle power assembly design and matching method - Google Patents
Heavy commercial vehicle power assembly design and matching method Download PDFInfo
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- CN113449405A CN113449405A CN202010217324.6A CN202010217324A CN113449405A CN 113449405 A CN113449405 A CN 113449405A CN 202010217324 A CN202010217324 A CN 202010217324A CN 113449405 A CN113449405 A CN 113449405A
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- 239000000446 fuel Substances 0.000 claims abstract description 9
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- 238000004088 simulation Methods 0.000 claims description 8
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- 238000004364 calculation method Methods 0.000 claims description 4
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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
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
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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
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H2061/0015—Transmission control for optimising fuel consumptions
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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
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H2061/0018—Transmission control for optimising exhaust emissions
Abstract
The invention provides a heavy commercial vehicle power assembly design and matching method, which is a set of power assembly design and matching method established based on the research on the working condition and the standard interpretation of vehicles in the market segments such as dump trucks and cargo trucks and the like and by combining the physical characteristics and the fuel consumption characteristics of heavy diesel engines. The optimal oil consumption and emission working area of an engine working rotating speed and a load area are determined mainly through road circulation and city circulation corresponding to the dump truck in a C-WTVVC circulation curve, and two design schemes of a 13-gear transmission and a 12-gear adjusting speed ratio of a 7 x 2 arrangement structure are formulated on the premise of ensuring client dynamic property (not changing a drive axle speed ratio, a maximum total speed ratio and the like) and using habits (driving and gear shifting habits) of users. The engine rotating speed can be effectively concentrated in the optimal working area when the dump truck and part of the truck run, and the aims of saving oil and reducing emission are fulfilled. Meanwhile, the ball gear area of the control handle of the transmission is redesigned, so that the driving experience is guaranteed.
Description
Technical Field
The invention relates to the technical field of automobile power assemblies, in particular to a heavy commercial vehicle power assembly design and matching method.
Background
The matching design of the power assembly of the heavy commercial vehicle generally refers to the development and matching design of key parts such as an engine, a clutch, a transmission, a drive axle and the like, and finally, the optimization of the dynamic property, the fuel economy, the pollutant emission and the like of the whole vehicle is realized.
In recent years, relevant policy and regulations in the heavy truck industry are intensively released, the energy-saving technology and emission upgrade of the heavy truck are accelerated, and the fuel consumption limit value and the emission regulations influence the development of vehicle power matching towards energy saving and low emission. The fuel consumption limit value required by the third stage of GB30510-2018 issued by Ministry of industry and communications is averagely reduced by 15% -18% compared with that required by the second stage, and the main pollutants in the sixth stage of GB17691 are reduced by more than 75% compared with that in the V stage of GB, and brand new requirements are provided for the design matching of an energy-saving emission-reducing technology and a whole vehicle power assembly. The existing part of vehicle type configurations in the heavy truck industry need subdividing engine data again according to working conditions, defining and developing the speed ratio of the transmission, and satisfying the requirements of regulation certification and realizing oil saving and emission reduction through a series of simulation and verification on the premise of ensuring dynamic property.
The difficulty in developing special engines for market subdivision is high, certain limitation exists, and the design of the operable power assembly matching design method for efficiently reducing oil consumption and emission becomes a strong demand in the development process of the six-country vehicle types. The inventor of the present invention has finally obtained the present invention through a long period of research and practice.
Disclosure of Invention
The invention provides a heavy commercial vehicle power assembly design and matching method, which has strong operability, can efficiently reduce oil consumption and emission, reaches the standard of national six-stage and three-stage oil consumption certification, shortens the design period of the national six-stage and brings economic benefits to users.
The technical scheme adopted by the invention is as follows:
a method for designing and matching the power assembly of heavy commercial vehicle is disclosed, which includes
determining the working area of optimal oil consumption and emission of the working speed and the load area of the engine on the premise of meeting the power matching requirement of users;
and 3, analyzing the dynamic property, the fuel economy and the emission by simulation calculation according to the matching combination of the working rotating speed area of the engine and the design of the transmission.
Further, the method further comprises:
and 4, repeatedly circulating the steps 1 to 3, adjusting the matching combination of the working rotating speed area of the engine and the design of the transmission, comparing the analysis results and determining the optimal matching combination.
In the step 1, the optimal oil consumption and emission working area of the engine working speed and load area is determined according to the road circulation and urban circulation corresponding to the dump truck in the GB 27840C-WTVVC circulation curve.
Illustratively, in step 2, the specific method for optimizing the transmission design is as follows:
the speed ratio of the existing 12-gear transmission is kept unchanged (1-12 gears are unchanged in climbing slope and dynamic property), an overdrive gear or a climbing gear is added to form a 13-gear transmission, and the 13 th gear is used when the vehicle is in a free return stroke or the vehicle speed is more than or equal to Vn (a certain specific vehicle speed).
Illustratively, the 13-speed transmission adopts a 7 × 2 arrangement, and the main box 7 is paired with forward gears, and the auxiliary box 2 is provided with speed ratios (low gear area and high gear area).
Illustratively, the main box 7 th pair of gears is locked in the low gear zone and is only used in the high gear zone; or the 1 st pair of forward gears is locked in the high gear range.
Illustratively, the range regions of the 13-speed transmission operating handle are arranged as follows:
aiming at the locking mode of the 7 th pair of gears of the main box in the low gear range, the leftmost side of the gear range of the control handle is reverse gear, and the rightmost side is 13 th gear;
in a mode of locking the 1 st pair of forward gear gears in the high gear range, the leftmost gear of the shift range of the control lever is a reverse gear and a climbing gear.
Illustratively, in step 2, the specific method for optimizing the transmission design is as follows:
the method is characterized in that the speed ratio of the first gear of the existing 12-gear transmission is kept unchanged (the maximum grade of the first gear is not changed, and the dynamic property of the first gear is not changed), the speed ratio and the grade difference of 2-12 gears are adjusted, and the 12 th gear is used when the empty vehicle returns or the vehicle speed is not less than Vn (a certain specific vehicle speed) on the premise of ensuring the dynamic property of the first gear.
Illustratively, the transmission employs a 6 × 2 arrangement.
Exemplarily, in the step 3, a new power matching frame under the same rule and comprehensive condition of the vehicle type is established based on AVL CRUISE software, and is analyzed and compared with the original configured simulation result and test result.
Because the power assembly configuration of the invention is optimized and analyzed based on the existing vehicle type configuration, the time for research and development of engine and transmission manufacturers is shortened, the requirements of six national vehicle types on oil consumption and emission can be met, and the competitiveness of the whole vehicle manufacturer is increased.
Drawings
In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings used in the description of the embodiments or the prior art will be briefly described below, and it is obvious that the drawings in the following description are some embodiments of the present invention, and other drawings can be obtained by those skilled in the art without creative efforts.
FIG. 1 is a C-WTVC cycle diagram of a heavy commercial vehicle;
FIG. 2 is a range layout of an operating handle for a 13 speed transmission in an embodiment of the present invention;
FIG. 3 is a range layout of another operating handle for a 13 speed transmission in an embodiment of the present invention;
FIG. 4 is a simplified layout of a 13 speed transmission (7 × 2 configuration) in one embodiment of the present invention;
FIG. 5 is a floor distribution diagram of an engine of an original scheme under the C-WTVVC working condition of the dump truck;
FIG. 6 is a diagram illustrating a floor profile of an engine under C-WTVC operation of a dump truck according to an embodiment of the present invention;
FIG. 7 is a block diagram of one embodiment of a heavy commercial vehicle powertrain design and mating method of the present invention.
Detailed Description
The above and further features and advantages of the present invention are described in more detail below with reference to the accompanying drawings.
In the description herein, references to the description of the term "one embodiment," "some embodiments," "an example," "a specific example," or "some examples," etc., mean that a particular feature, structure, material, or characteristic described in connection with the embodiment or example is included in at least one embodiment or example of the invention. In this specification, the schematic representations of the terms used above are not necessarily intended to refer to the same embodiment or example. Furthermore, the particular features, structures, materials, or characteristics described may be combined in any suitable manner in any one or more embodiments or examples. Furthermore, various embodiments or examples and features of different embodiments or examples described in this specification can be combined and combined by one skilled in the art without contradiction.
In this embodiment, aiming at heavy commercial self-discharging and special vehicle type configuration which is difficult to satisfy the regulation limit value, the actual measurement emission and oil consumption values are analyzed, and on the premise of ensuring the customer dynamic property (without changing the speed ratio of a drive axle, the maximum total speed ratio and the like) and the use habits (driving and gear shifting habits) of a user, the optimal oil saving and emission area rotating speed of the engine is combined, and the principle of adjusting the highest gear speed ratio of the transmission is matched for presetting:
1. optimizing the working speed and load area of the engine: referring to fig. 1, 5 and 6, according to a GB 27840C-WTVC circulation curve (see fig. 1), the dump truck corresponds to road circulation and urban circulation, the vehicle speed is 0-72 km/h, and the corresponding main working rotation speed area of the engine is n-n +900rpm (see fig. 5). The optimal oil consumption and emission working speed area of the engine is n-n +500 rpm; after the highest gear speed ratio of the transmission is optimized, the working rotating speed and the load area of the engine are concentrated in the optimal working area n-n +500rpm of the engine (see figure 6), and meanwhile, for an engine factory, the development difficulty of a special engine for market subdivision is reduced, but the contribution to oil consumption and emission is equivalent to the development of the special engine;
2. based on the existing 12-gear box type speed ratio and the step difference, two transmission speed ratio design schemes are adopted: the first scheme is that 1 highest gear is added on the premise that the existing 12-gear speed ratio and the existing step difference are kept unchanged: the 13 th gear (overdrive gear) can be used when the idle return stroke or the vehicle speed is not less than Vn (certain specific vehicle speed) on the premise of ensuring the dynamic property of the 1-12 gears and the habit of users; and in the second scheme, on the premise of keeping the conventional first gear speed ratio, the 2-12 gear speed ratio is adjusted, the step difference is enlarged, the 12 th gear speed ratio is reduced, and the 12 th gear is used when the empty vehicle returns or the vehicle speed is more than or equal to Vn on the premise of ensuring the dynamic property of the first gear.
As shown in fig. 2 to 4, for the first scheme, a 7 × 2 arrangement structure (see fig. 4) is adopted for the 13-speed transmission, and a main box 7 can combine 14 forward speeds for forward speed gears and a sub-box 2 sets of speed ratios (low-speed and high-speed areas). The 7 th pair of gears of the main box needs to be locked in a low gear area and only used in a high gear area, the gear area is arranged in a mode (see fig. 2), the leftmost side is reverse gear, and the rightmost side is 13 gears; or the 1 st pair of forward gears are locked in the high gear range, the arrangement mode of the 13-gear range can be changed into reverse gear and climbing gear on the leftmost side, and the rest arrangement is the same as that of the existing 12-gear box range (see fig. 3).
The 7 x 2 arrangement structure of the 13-gear transmission can be designed to ensure that the combined speed ratio of the 7 th pair of forward gears and the low gear of the auxiliary box of the main box is the same as the combined speed ratio of the 1 st pair of forward gears and the high gear of the auxiliary box of the main box, so that the arrangement modes of the two gear areas can be ensured, the speed ratio differences of all gears of the new 13-gear transmission can be ensured to be the same or similar no matter the 7 th pair of gears of the main box are locked in the low gear area or the 1 st pair of gears are locked in the high gear area, the gear areas of 1-12 gears and man-machine remain unchanged with the prior art, and the comfort of the transmission and the whole vehicle can be improved.
3. According to the matching method, a new power matching frame under the same rule comprehensive working condition of the vehicle type is established based on AVL CRUISE software, the power performance and the fuel economy of the method are analyzed, and compared with the originally configured simulation result and test result, particularly whether the comparison of the economic fuel consumption area is improved or not is judged.
The preset matching can be adjusted for many times according to the method, and the combination of the engine limited working speed and the gearbox speed ratio meeting the conditions is determined through simulation calculation, so that the optimal power assembly configuration is obtained quickly. Because the power assembly configuration generated by the embodiment of the invention is optimized and analyzed for the configuration of the existing vehicle type, the time for research and development of engine and transmission manufacturers is shortened, the requirements of the six national vehicle types on oil consumption and emission can be met, and the competitiveness of the whole vehicle factory is increased.
In a more specific embodiment, taking the existing whole vehicle model as an example (the six-country dump vehicle model of shanxi ma X5000, M5000, X3000 or M30008 × 4/WP 12 engine/F12 gear box/5.262 axle speed ratio), matching is performed according to the method of the invention, and the specific steps are as follows:
1. the range of the main working rotating speed interval of the engine is limited to be changed from 900rpm to 500rpm, and the original 5.262 bridge speed ratio is matched;
2. and (4) carrying out range analysis on the gear area of the existing 12-gear box, and calculating and increasing 13 gears according to the range. The speed ratio distribution can be carried out by setting the range of the first gear speed ratio to be 15-15.6, the highest gear speed ratio to be 0.73-0.8 and setting the range speed ratio to be +/-0.02 of the original 12-gear box.
(1) The following example is a 13-gear box gear area arrangement mode, which is the first type in fig. 5, and the ratio distribution is calculated by using the original range difference of 1.28:
the main box speed ratio is as follows:
| |
1 st pair | No. 2 to | No. 3 to | No. 4 to | No. 5 to | No. 6 to | 7 th pair |
| Main box velocity ratio distribution | 3.48 | 2.71 | 2.1 | 1.64 | 1.28 | 1 | 0.78 |
The speed ratios of the auxiliary box 2 groups and the reverse gear speed ratio are as follows:
the main box and the auxiliary box of the transmission are arranged by 7 multiplied by 2, the main box adopts a double-intermediate shaft structure, the 7 th counter gear of the main box is locked in a low gear area, only a high gear area (0.78) is reserved to be a 13-gear speed ratio, the 13-gear is only used when the vehicle speed is more than Vn, and the gear shifting operation is the same as the existing 12-gear when the vehicle speed is less than or equal to Vn, so that the influence on the use habit of a user is small.
(2) The following example is a gear arrangement such as the second in fig. 5, with the range still being 1.28 to make the calculated ratio distribution:
the main box and the auxiliary box of the transmission are arranged by 7 multiplied by 2, the main box adopts a double-intermediate-shaft structure, the speed ratio of the main box, the speed ratio of 2 groups of the auxiliary box and the reverse gear speed ratio are the same as the above example, but the 1 st pair of gears are locked in a high gear area, and only a low gear area (15.53) is reserved as a climbing gear C gear.
3. Through simulation calculation of AVL CRUISE software under the C-WTVC circulation condition, analysis and comparison are as follows (see fig. 5 and 6), and the results show that:
(1) reducing the operating speed of the engine increases the high load ratio in the corresponding speed region;
(2) the oil consumption is reduced by 1.2-1.5L/100 km, and the limit value (less than or equal to 41L/100km) of the fuel consumption (GB30510) of the heavy commercial dump truck can be met;
(3) the main working speed interval of the engine is changed into 500rpm, so that the emission of the engine is easy to control, and the Pems emission of the whole vehicle is easier to pass;
(4) if the main operating speed interval of the engine is 500rpm, the development difficulty of the special engine for market division is reduced (the optimal speed range determined by the mechanical characteristics of the supercharger is determined), and the contribution to the oil consumption is increased.
In conclusion, as shown in fig. 7, the heavy-duty commercial vehicle power assembly design and matching method can reduce oil consumption and emission of heavy-duty commercial dump trucks and special-purpose vehicles, so that the requirements of regulation limit values such as GB30510-2018 (three stages) and GB17691-2018 (six stages in China) are met; firstly, on the premise of meeting the requirement of power matching used by a user, the running rotating speed range of the engine is controlled in the working rotating speed and load state with optimal oil consumption and emission by optimizing the speed ratio of the transmission. The method is characterized in that the speed ratio of the existing 12-gear transmission is kept unchanged (1-12 gears are unchanged in climbing slope and dynamic property), and an overdrive gear or a climbing gear is designed and added to form a 13-gear transmission; or the existing 12-gear transmission is kept unchanged in first gear speed ratio (the maximum grade of climbing of the first gear and the dynamic property are unchanged), and 2-12 gear speed ratio and grade difference are adjusted to form a new 12-gear transmission so as to reduce the running rotating speed of the engine to the optimal working rotating speed, and at the moment, the oil consumption and the emission of the engine and the whole vehicle are in the optimal state. The 13-gear transmission adopts a 7 x 2 arrangement structure, a main box 7 is used for forward gear gears, and the auxiliary box 2 groups of speed ratios (low gear and high gear are direct gears); determining the speed ratio distribution of a group of 13-gear transmissions, wherein the range of the first gear speed ratio is determined to be 15-15.6, the range of the highest gear speed ratio is determined to be 0.73-0.8, the range of the highest gear speed ratio is determined to be +/-0.02 of the original range ratio, and the range is calculated. The 12-gear speed changer adopts a 6 multiplied by 2 arrangement structure, the range of the first gear speed ratio is determined to be 15-15.6, the range of the highest gear speed ratio is determined to be 0.73-0.8, the range of the extreme difference is determined to be 1.32 +/-0.02, and the calculated speed ratio distribution of a group of 12-gear speed changers is calculated. According to the new 13-gear transmission matched by the method, the 7 th pair of gears of the main box is locked in a low gear range, or the 1 st pair of gears of the main box is locked in a high gear range, so that the 1-12 gear range of common gears and the man-machine optimization can be ensured. Two kinds of fender regions of 13 keep off derailleur control handle ball arrange, and the first one is for the leftmost fender that is reverse gear, and the rightmost side is 13 keeps off, and the second one is for the leftmost fender that is reverse gear and climbing fender, and the remaining is arranged and is the same with current 12 fender casees keep off the region.
The foregoing is merely a preferred embodiment of this invention, which is intended to be illustrative, and not limiting. The structure, the connection mode and the like of all the components in the invention can be changed, and the equivalent transformation and the improvement on the basis of the technical scheme of the invention are not excluded from the protection scope of the invention.
Claims (10)
1. A heavy commercial vehicle power assembly design and matching method comprises
Step 1, optimizing the working rotating speed and load area of an engine:
determining the working area of optimal oil consumption and emission of the working speed and the load area of the engine on the premise of meeting the power matching requirement of users;
step 2, optimizing the design of the transmission according to the determined optimal working rotating speed area of the engine;
and 3, analyzing the dynamic property, the fuel economy and the emission by simulation calculation according to the matching combination of the working rotating speed area of the engine and the design of the transmission.
2. The method of designing and matching a heavy commercial vehicle powertrain of claim 1, further comprising:
and 4, repeatedly circulating the steps 1 to 3, adjusting the matching combination of the working rotating speed area of the engine and the design of the transmission, comparing the analysis results and determining the optimal matching combination.
3. The method for designing and matching the power assembly of the heavy-duty commercial vehicle according to claim 1, wherein in the step 1, the working area with the optimal oil consumption and emission in the engine working speed and load area is determined according to the road circulation and the urban area circulation of the dump truck in the GB 27840C-WTVVC circulation curve.
4. The method for designing and matching the power assembly of a heavy commercial vehicle according to claim 1, wherein in the step 2, the specific method for optimizing the design of the transmission is as follows:
the speed ratio of the existing 12-gear transmission is kept unchanged (1-12 gears are unchanged in climbing slope and dynamic property), an overdrive gear or a climbing gear is added to form a 13-gear transmission, and the 13 th gear is used when the vehicle is in a free return stroke or the vehicle speed is more than or equal to Vn (a certain specific vehicle speed).
5. The method of claim 4, wherein the 13-speed transmission is arranged in a 7 x 2 configuration, and the main box is 7 pairs of forward gears, and the auxiliary box is 2 sets of speed ratios (low range and high range).
6. The method of claim 5, wherein the 7 th pair of gears of the main box are locked in the low gear range and only used in the high gear range; or the 1 st pair of forward gears is locked in the high gear range.
7. The method of claim 6, wherein the range of the 13-speed transmission handle is arranged to:
aiming at the locking mode of the 7 th pair of gears of the main box in the low gear range, the leftmost side of the gear range of the control handle is reverse gear, and the rightmost side is 13 th gear;
in a mode of locking the 1 st pair of forward gear gears in the high gear range, the leftmost gear of the shift range of the control lever is a reverse gear and a climbing gear.
8. The method for designing and matching the power assembly of a heavy commercial vehicle according to claim 1, wherein in the step 2, the specific method for optimizing the design of the transmission is as follows:
the method is characterized in that the speed ratio of the first gear of the existing 12-gear transmission is kept unchanged (the maximum grade of the first gear is not changed, and the dynamic property of the first gear is not changed), the speed ratio and the grade difference of 2-12 gears are adjusted, and the 12 th gear is used when the empty vehicle returns or the vehicle speed is not less than Vn (a certain specific vehicle speed) on the premise of ensuring the dynamic property of the first gear.
9. The method of claim 8, wherein the transmission is configured in a 6 x 2 arrangement.
10. The method as claimed in claim 1, wherein in step 3, a new power matching framework under the same rule and comprehensive conditions of the vehicle type is established based on AVL CRUISE software, analyzed, and compared with the original configured simulation results and test results.
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