CN113449405B - 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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- CN113449405B CN113449405B CN202010217324.6A CN202010217324A CN113449405B CN 113449405 B CN113449405 B CN 113449405B CN 202010217324 A CN202010217324 A CN 202010217324A CN 113449405 B CN113449405 B CN 113449405B
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- 230000005540 biological transmission Effects 0.000 claims abstract description 47
- 239000000446 fuel Substances 0.000 claims abstract description 15
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- 230000002441 reversible effect Effects 0.000 claims description 8
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- 238000004458 analytical method Methods 0.000 claims description 5
- 238000004364 calculation method Methods 0.000 claims description 4
- 238000012360 testing method Methods 0.000 claims description 3
- 230000001351 cycling effect Effects 0.000 claims description 2
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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
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Abstract
The invention provides a design and matching method of a power assembly of a heavy-duty commercial vehicle, which is a set of power assembly design and matching method based on working condition research and standard interpretation research of vehicles in market segments such as dumpers, trucks and the like and combining physical characteristics and fuel consumption characteristics of a heavy-duty diesel engine. The working areas of the optimal oil consumption and emission of the engine working speed and the load area are determined mainly through the corresponding highway circulation and urban area circulation of the dump truck in the C-WTVC circulation curve, and two designs of a 13-gear transmission and a 12-gear adjusting speed ratio of a 7 multiplied by 2 arrangement structure are formulated on the premise of ensuring the dynamic performance of a client (not changing the speed ratio of a drive axle, the maximum total speed ratio and the like) and the use habit of a user (driving and gear shifting habit). The engine speed of the dump truck and part of the truck can be effectively concentrated in the optimal working area when the dump truck and part of the truck run, and the purposes of saving oil and reducing emission are achieved. Meanwhile, the ball blocking area of the transmission control handle is redesigned, and driving experience is guaranteed.
Description
Technical Field
The invention relates to the technical field of automobile power assemblies, in particular to a design and matching method of a heavy-duty commercial automobile power assembly.
Background
The matched design of the power assembly of the heavy commercial vehicle generally refers to the development and matched design of key parts such as an engine, a clutch, a transmission, a drive axle and the like, and finally, the optimization of the power performance, the fuel economy, the pollutant emission and the like of the whole vehicle is realized.
In recent years, related policies and regulations of the heavy truck industry are intensively released, the heavy truck energy saving technology and emission upgrading are accelerated, and the fuel consumption limit value and the emission regulation influence the development of vehicle power matching to energy saving and low emission. The third stage of GB30510-2018 issued by the industrial information department requires that the fuel consumption limit value is reduced by 15% -18% compared with the second stage, and the main pollutants in the six stages of GB17691 are reduced by more than 75% compared with the main pollutants in the V stage, so that brand new requirements are provided for the energy conservation and emission reduction technology and the design and matching of the whole vehicle power assembly. The existing part of vehicle type configuration in the heavy truck industry needs to subdivide engine data according to working conditions, the speed ratio of the transmission is defined and developed, and the requirements of regulation authentication are met under the premise of ensuring dynamic performance through a series of simulation and verification, so that oil saving and emission reduction are realized.
The difficulty of developing and market-breaking special engines is high and certain limitation exists, and the design method for matching the power assembly with the operable high-efficiency oil consumption reduction and emission is a strong demand in the development process of six Chinese models. The present inventors have finally achieved the present invention through long-time studies and practices.
Disclosure of Invention
The invention provides a design and matching method of a heavy commercial vehicle power assembly, which has strong operability, can efficiently reduce oil consumption and emission, achieves the national standard of six-emission and three-stage oil consumption authentication, shortens the design period of the national six-stage fuel consumption, and brings economic benefit to users.
The invention adopts the technical scheme that:
the utility model provides a heavy commercial vehicle power assembly design and matching method, which comprises the following steps of
Step 1, optimizing the working speed and load area of an engine:
On the premise of meeting the power matching used by a user, determining the working speed of the engine and the working area of optimal oil consumption and emission of a load area;
step 2, optimizing the design of the transmission according to the determined optimal working speed area of the engine;
And 3, analyzing the dynamic property, the fuel economy and the emission through simulation calculation according to the matching combination of the engine working speed region and the transmission design.
Further, the method further comprises:
And 4, repeatedly cycling the steps 1 to 3, adjusting the matching combination of the engine working speed area and the design of the transmission, and comparing analysis results to determine the optimal matching combination.
In the step 1, the working area of optimal oil consumption and emission of the engine working speed and load area is determined according to the road circulation and the urban circulation corresponding to the dump truck in the GB 27840C-WTVC circulation curve.
Illustratively, in step 2, the specific method of optimizing the transmission design is:
The speed ratio of the existing 12-gear transmission is kept unchanged (the climbing gradient of the gear 1-12 and the dynamic property are unchanged), an overdrive gear or climbing gear is added to form a 13-gear transmission, and the 13 th gear is used when the idle stroke or the vehicle speed is more than or equal to Vn (a certain specific vehicle speed).
Illustratively, a 13-speed transmission employs a 7 x 2 arrangement with main case 7 versus forward gear, and sub-case 2 sets of speed ratios (low range, high range).
Illustratively, the main box 7 th pair gear is locked in the low gear region and is only used in the high gear region; or the 1 st pair of forward gears is locked in the high gear region.
Illustratively, the shift region of the 13-speed transmission lever is arranged as:
aiming at the mode that the 7 th pair of gears of the main box are locked in the low gear region, the leftmost side of the gear region of the control handle is a reverse gear, and the rightmost side is a 13 th gear;
The leftmost side of the gear area of the control handle is a reverse gear and a climbing gear aiming at the mode of locking the 1 st pair of forward gears in the high gear area.
Illustratively, in step 2, the specific method of optimizing the transmission design is:
the speed ratio of the head gear of the existing 12-gear transmission is kept unchanged (the maximum climbing gradient and the dynamic property of the head gear are unchanged), the speed ratio and the step of the 2-12 gears are adjusted, and the 12 th gear is used when the idle speed or the vehicle speed is more than or equal to Vn (certain specific vehicle speed) on the premise of guaranteeing the dynamic property of the head gear.
Illustratively, the transmission employs a 6 x 2 arrangement.
In the step 3, a new power matching frame under the same legal and comprehensive working conditions of the vehicle type is established based on AVL CRUISE software, and analysis is performed, and comparison is performed with the simulation result and the test result of the original configuration.
Because the power assembly configuration of the invention is optimized and analyzed based on the existing vehicle type configuration, the development time of engine and transmission manufacturers is shortened, the requirements of six vehicle types on oil consumption and emission can be met, and the competitiveness of the whole vehicle manufacturer is improved.
Drawings
In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings that are needed in the description of the embodiments or the prior art will be briefly described, and it is obvious that the drawings in the description below are some embodiments of the present invention, and other drawings can be obtained according to the drawings without inventive effort for a person skilled in the art.
FIG. 1 is a diagram of a heavy commercial vehicle C-WTVC cycle;
FIG. 2 is a range layout of a lever of a 13-speed transmission in one embodiment of the present invention;
FIG. 3 is a range layout of another shifter handle for a 13-speed transmission in one embodiment of the present invention;
FIG. 4 is a schematic illustration of the arrangement of a 13-speed transmission (7X 2 configuration) in one embodiment of the invention;
FIG. 5 is a diagram of the original engine floor profile for the dump truck C-WTVC operating mode;
FIG. 6 is a graph showing a landing profile of a dump truck C-WTVC operating mode engine according to an embodiment of the present invention;
FIG. 7 is a block diagram of one embodiment of a heavy duty commercial vehicle powertrain design and matching method of the present invention.
Detailed Description
The above and further technical features and advantages of the present invention are described in more detail below with reference to the accompanying drawings.
In the description of the present specification, a description referring to terms "one embodiment," "some embodiments," "examples," "specific examples," or "some examples," etc., means 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 present invention. In this specification, schematic representations of the above terms are not necessarily directed 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, the different embodiments or examples described in this specification and the features of the different embodiments or examples may be combined and combined by those skilled in the art without contradiction.
In this embodiment, for the configuration of heavy commercial self-unloading and special vehicle types which are difficult to meet the regulation limit, the measured emission and oil consumption values are analyzed, and under the premise of ensuring the dynamic performance of a customer (without changing the speed ratio of a drive axle, the maximum total speed ratio and the like) and the use habit of a user (driving and gear shifting habit), the optimal fuel saving and emission area rotating speed of an engine is combined, and the principle of adjusting the highest gear ratio of a 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 the cycle curve of GB 27840C-WTVC (see fig. 1), the dumper corresponds to highway cycle and urban cycle, the speed of the vehicle is 0-72 km/h, and the main working speed area of the corresponding engine is n-n+900 rpm (see fig. 5). The optimal oil consumption and the emission working rotating speed area of the engine are n-n+500 rpm; after the highest gear ratio of the transmission is optimized, the working speed and load area of the engine are concentrated in the optimal working area n-n+500 rpm (see figure 6), meanwhile, the development difficulty of the special engine for the market segment is reduced for an engine factory, but the contribution to oil consumption and emission is equivalent to that of the special engine;
2. Based on the existing 12-gear box speed ratio and step, two speed ratio design schemes of the transmission are as follows: according to the first scheme, under the premise that the existing 12-gear speed ratio and step difference are kept unchanged, 1 highest gear is increased: the 13 th gear (overdrive gear) can ensure the power performance of the 1-12 gears and the habit of a user, and the 13 th gear is used when the idle car returns or the vehicle speed is more than or equal to Vn (certain specific vehicle speed); in the second scheme, on the premise of keeping the existing first gear speed ratio, the 2-12 gear speed ratio is adjusted, the step is enlarged, the 12 th gear speed ratio is reduced, and on the premise of guaranteeing the first gear power performance, the 12 th gear is used when the idle stroke or the vehicle speed is more than or equal to Vn.
As shown in fig. 2 to 4, for the first scheme, a 13-speed transmission adopts a 7×2 arrangement structure (see fig. 4), and the main case 7 is configured to combine with 14 forward gears for forward gear, and the auxiliary case 2 is configured to combine with a group speed ratio (low-speed, high-speed region). The 7 th pair of gears of the main box are required to be locked in a low gear area and are only used in a high gear area, the arrangement mode of the gear areas (see figure 2) is that the leftmost side is a reverse gear, and the rightmost side is a 13 gear; or the 1 st pair of forward gears are locked in the high gear area, the arrangement mode of the 13-gear area can be changed into reverse gear and climbing gear at the leftmost side, and the rest arrangement is the same as that of the existing 12-gear box gear area (see figure 3).
The 7 multiplied by 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 of the main box and the low gear of the auxiliary box is the same as the combined speed ratio of the 1 st pair of forward gears of the main box and the high gear of the auxiliary box, thus ensuring the arrangement modes of the two gear areas, ensuring that the gear ratio steps of the new 13-gear transmission are the same or similar no matter when 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, keeping the 1-12-gear area and the man-machine unchanged from the prior art, and improving the comfort of the transmission and the whole car.
3. According to the matching method, a new power matching framework under the same legal and comprehensive working conditions of the vehicle type is established based on AVL CRUISE software, the power performance and the fuel economy of the method are analyzed, and the power matching framework is compared with the simulation result and the test result of the original configuration, in particular whether the comparison of the economic fuel consumption area is improved or not.
The method can adjust preset matching for a plurality of times according to the method, and determines the combination of the engine limiting working speed and the speed ratio of the gearbox meeting the conditions through simulation calculation, so that the optimal power assembly configuration is obtained rapidly. The power assembly generated by the embodiment of the invention is configured for the optimization analysis of the existing vehicle type configuration, so that the development time 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 manufacturer is improved.
In a more specific embodiment, taking the existing whole vehicle model as an example (taking the six dumper model of Shaanxi, X5000, M5000, X3000 or M3000 8*4 China/WP 12 engine/F12 gear box/5.262 bridge speed ratio) for matching according to the method, 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 (3) performing range analysis on the existing 12-gear box baffle region, and calculating the added 13 gears according to the range. The range of the first gear speed ratio is 15-15.6, the highest gear speed ratio is 0.73-0.8, and the range speed ratio is determined as the range of the original 12 gear box plus or minus 0.02 to perform speed ratio distribution.
(1) The arrangement mode of the 13-gear box baffle zone in the following example is as shown in the first mode of fig. 5, and the calculated speed ratio distribution is calculated by using the original range of 1.28:
The main box speed ratio is as follows:
| Forward gear | Pair 1 | Pair 2 | Pair 3 | Fourth pair 4 | 5 Th pair | 6 Th pair | Pair 7 |
| Main box speed ratio distribution | 3.48 | 2.71 | 2.1 | 1.64 | 1.28 | 1 | 0.78 |
The group 2 speed ratio and the reverse speed ratio of the auxiliary box are as follows:
The transmission main box and the auxiliary box are arranged in a mode of 7 multiplied by 2, the main box adopts a double-intermediate-shaft structure, the 7 th pair of gears of the main box are locked in a low gear region, only a high gear region (0.78) is reserved to be a 13-gear speed ratio, the 13-gear is used only when the vehicle speed is more than or equal to Vn, the gear shifting operation is similar to the existing 12-gear when the vehicle speed is less than or equal to Vn, and the influence on the use habit of a user is small.
(2) The following example is a gear arrangement as in the second embodiment of fig. 5, with a range of still 1.28 to make the estimated speed ratio distribution:
The main box and the auxiliary box of the transmission are arranged in a mode of 7 multiplied by 2, the main box adopts a double intermediate shaft structure, the speed ratio of the main box, the speed ratio of the group 2 of the auxiliary box and the reverse gear speed ratio are the same as those of the previous example, but the 1 st pair of gears are locked in the high gear area, and only the low gear area (15.53) is reserved as the climbing gear C.
3. Simulation calculation under the C-WTVC loop working condition by the AVL CRUISE software, analysis and comparison are as follows (see FIG. 5 and FIG. 6), and the result is found:
(1) Decreasing the engine operating speed increases the high load duty cycle in the corresponding speed zone;
(2) The fuel consumption is reduced by 1.2-1.5L/100 km, and the limit value (less than or equal to 41L/100 km) of the fuel consumption (GB 30510) of the heavy commercial dump truck can be met;
(3) Because the main working speed interval of the engine is changed to 500rpm, the emission of the engine is easy to control, and the emission of the whole vehicle Pems is easier to pass;
(4) If the main engine operating speed range is 500rpm, development difficulty for the engine dedicated to the market segment is reduced (the optimum speed range determined by the mechanical characteristics of the supercharger is determined), and the contribution to fuel consumption is increased.
In summary, as shown in fig. 7, the design and matching method of the power assembly of the heavy commercial vehicle can reduce the oil consumption and emission of the heavy commercial dump truck and the special vehicle, thereby meeting the requirement of the regulatory limit values such as GB30510-2018 (three phases), GB17691-2018 (six phases of China) and the like; firstly, on the premise of meeting the power matching used by a user, the running speed range of the engine is controlled to be in the working speed and load state of optimal oil consumption and emission by optimizing the speed ratio of the transmission. The existing 12-gear speed changer is kept unchanged in speed ratio (1-12-gear climbing gradient and dynamic property are unchanged), and an overdrive gear or climbing gear is designed to be added to form a 13-gear speed changer; or the head gear speed ratio of the existing 12-gear speed changer is kept unchanged (the maximum climbing gradient of the head gear and the dynamic property are unchanged), the 2-12-gear speed ratio and the step difference are adjusted, and the novel 12-gear speed changer is formed, so that the running speed of the engine is reduced to the optimal working speed, and the fuel consumption and the emission of the engine and the whole vehicle are in the optimal state. The 13-gear speed changer adopts a 7 multiplied by 2 arrangement structure, a main box 7 pairs forward gear and a subsidiary box 2 sets of speed ratios (a low gear and a high gear are direct gears); the range of the head 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 is determined to be the original range speed ratio plus or minus 0.02, and the calculated speed ratio distribution of the 13-gear transmission is calculated. The 12-gear speed changer adopts a 6 multiplied by 2 arrangement structure, the range of the head 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 difference is determined to be 1.32+/-0.02, and the calculated speed ratio distribution of the 12-gear speed changer is calculated. According to the new 13-gear transmission matched by the method, the 7 th pair of gears of the main box are locked in a low gear area, or the 1 st pair of gears of the main box are locked in a high gear area, so that the common gear 1-12 gear area and the man-machine optimization can be ensured. The two gear areas of the 13-gear transmission control handle ball are arranged, wherein the first gear is the leftmost gear, the rightmost gear is the 13 gear, the second gear is the leftmost gear and the climbing gear, and the rest arrangement is the same as that of the existing 12-gear box gear area.
The foregoing description of the preferred embodiment of the invention is merely illustrative of the invention, and is not intended to be limiting. The structure, connection mode and the like of each component in the invention can be changed, and all equivalent changes and improvements performed on the basis of the technical scheme of the invention are not excluded from the protection scope of the invention.
Claims (8)
1. A heavy duty commercial vehicle powertrain design and matching method comprising:
Step 1, optimizing the working speed and load area of an engine:
On the premise of meeting the power matching used by a user, determining the working speed of the engine and the working area of optimal oil consumption and emission of a load area;
Step 2, optimizing the design of the transmission according to the determined optimal working speed area of the engine; the specific method for optimizing the design of the transmission is one of the following two methods:
Method (1): the speed ratio of the existing 12-speed transmission is kept unchanged: the 1-12 gear climbing gradient and the dynamic property are unchanged, an overdrive gear or climbing gear is added to form a 13 gear transmission, and the 13 th gear is used when the idle stroke or the vehicle speed is more than or equal to Vn, wherein the Vn is a specific vehicle speed;
Method (2): the gear ratio of the head of the existing 12-gear transmission is kept unchanged: the maximum climbing gradient and the dynamic property of the first gear are unchanged, the speed ratio and the step difference of the 2-12 gears are adjusted, and the 12 th gear is used when the idle travel or the vehicle speed is more than or equal to Vn on the premise of guaranteeing the dynamic property of the first gear, wherein the Vn is a certain specific vehicle speed;
And 3, analyzing the dynamic property, the fuel economy and the emission through simulation calculation according to the matching combination of the engine working speed region and the transmission design.
2. The heavy-duty commercial vehicle powertrain design and matching method of claim 1, further comprising:
And 4, repeatedly cycling the steps 1 to 3, adjusting the matching combination of the engine working speed area and the design of the transmission, and comparing analysis results to determine the optimal matching combination.
3. The method for designing and matching a power assembly of a heavy-duty commercial vehicle according to claim 1, wherein in the step 1, the working areas of optimal fuel consumption and emission of the engine working speed and load area are determined according to the road circulation and the urban circulation corresponding to the dump truck in the GB 27840C-WTVC circulation curve.
4. A heavy duty commercial vehicle powertrain design and matching method according to claim 1, characterized in that in said step 2, for the method (1) of optimizing transmission design: the 13-gear transmission adopts a 7 multiplied by 2 arrangement structure, the main box 7 is used for driving gear, and the auxiliary box 2 is provided with a group of speed ratios: i.e. the low range and the high range.
5. A heavy duty commercial vehicle powertrain design and matching method as claimed in claim 4, wherein in said step 2, for the method of optimizing transmission design (1): the 7 th pair of gears of the main box are locked in a low gear area and are only used in a high gear area; or the 1 st pair of forward gears is locked in the high gear region.
6. A heavy duty commercial vehicle powertrain design and matching method as claimed in claim 5, wherein in said step 2, for the method of optimizing transmission design (1): the gear area of the 13-speed transmission operating handle is arranged as follows:
aiming at the mode that the 7 th pair of gears of the main box are locked in the low gear region, the leftmost side of the gear region of the control handle is a reverse gear, and the rightmost side is a 13 th gear;
The leftmost side of the gear area of the control handle is a reverse gear and a climbing gear aiming at the mode of locking the 1 st pair of forward gears in the high gear area.
7. A heavy duty commercial vehicle powertrain design and adaptation method according to claim 1, characterized in that in said step 2, for the method (2) of optimizing the transmission design: the transmission adopts a 6×2 arrangement.
8. The method for designing and matching the power assembly of the heavy commercial vehicle according to claim 1, wherein in the step 3, a new power matching frame is built under the same legal and comprehensive working conditions of the vehicle type based on AVL CRUISE software, and is analyzed and compared with simulation results and test results of the original configuration.
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