giới thiệu đôi chút về dòng xe huyndai tucson

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Phan Trung Dũng

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<i>I.Giới thiệu đôi chút về dịng xe </i>

•Tucson là mẫu xe SUV hạng C có tính đa dụng, tiện nghi và sang trọng nhất ở thị trường Việt Nam, kết hợp sự năng động, mạnh mẽ đặc trưng của dịng xe SUV cùng khơng gian sang trọng, tiện nghi, ứng dụng nhiều công nghệ hiện đại tạo nên chuẩn mực mới trong phân khúc SUV.

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II. Bố trí tuyến hình

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III. - Basic dimensions of the car:

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<b>3.1 )Thông số theo thiết kế phác thảo</b>

III.Thông số đầu vào

-Engine type: 2.0L I4 Smartstream naturally aspirated gasoline engine

-Displacement: V

_c

= 1999 (cc)

-Maximum power: P

_max

= 156 (horsepower)-n

_N

: 6200 (rpm) (revolutions per minute)-Maximum torque: M

_max

= 192 (Nm)

-Maximum speed: V

_max

= 230(km/h) = 63,9 (m/s)-Power transmission system:

Front – mounted engine, front – wheel drive 6 – speed automatic transmission

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III.Thông số đầu vào-Self weight: 1576kg

-Passenger weight: 60kg/ person-Luggage weight: 20kg/ person-Power transmission efficiency: 0,95-Air resistance coefficient: K = 0,18

-Rolling resistance coefficient when V < 22 m/s is f

₀

= 0,01 

<b>3.2 Thông số chọn</b>

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III.Thông số đầu vào

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-Dynamic and kinematic radius of the wheel: r

_b

= r

_k

= λ r

₀

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III.Thông số đầu vào

<small>- </small> <i><small>Vehicle: Hyundai Tucson 2.0 special version with 5 seats: </small></i>

<small>- </small> <i><small>Curb weight (Vehicle own’s weight): G0 = 1576 (kg) </small></i>

<small>- </small> <i><small>Payload (Cargo, luggage,..): Gh = 20 (kg) </small></i>

<small>- </small> <i><small>Weight: </small></i>

G – Curb weight

n – number of people (n=5) A – Weight of each person G<small>h</small> – Weight of luggage

<small>- </small> <i><small>G = 1576 + 5.(60 + 20) = 1976 (kg) </small></i>

<small> </small> <i><small>So the total weight of the vehicle: G = 1976 (kg) = 19760 (N) </small></i>

<small> </small> <i><small>Weight distribution: the load weight of the car acting on the front axle (G1) accounts for (55% ÷ 65%).G </small></i>

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IV.Xây dựng đường đặc tính ngoài của động cơ

<small>- </small> <i><small>The external speed characteristics curve of the engine represents relationship between power, torque and fuel consumption of the engine according to the engine’s rotational speed. These characteristic curves include: </small></i>

<small>w</small>_{e N}<i><small> . For an unrestricted – speed gasoline engine </small></i>

<small>- </small> <i><small>Choose λ = 1 (for gasoline engine) </small></i>

(N<small>e</small>)<small>max</small> = ^𝑁<small>𝑒𝑣</small>

<small>𝑎 .൬</small>^{𝑤 𝑒𝑣}

<small>𝑤 𝑒𝑁</small>^൰^{+𝑏 .൬}<small>𝑤 𝑒𝑣𝑤 𝑒𝑁</small>^൰

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IV. Xây dựng đường đặc tính ngồi của động cơ

<i>- V</i>

<i><small>max</small></i>

<i> = 230 (km/h) = 63,9 (m/s) > 22 (m/s). So the rolling resistance coefficient f is caculated as: </i>

𝑓 = 𝑓

₀

∗ቀ1 +

^𝑉<small>𝑚𝑎𝑥</small> ²

<small>1500</small>

<i>ቁ ⇒ f = 0,01 . ቀ1 +</i>

^63,9²

<small>1500</small>

ቁ = 0,0372 Where:

<i>- K – Air resistance coefficient (K = 0,18) - F – Frontal area </i>

<i>- η</i>

<i>_tl</i>

<i> – Power transmission efficiency (η</i>

<i>_tl</i>

<i> = 0,95) </i>

- 

<i><small>max</small></i>

<i> – Total coefficient of road resistance (</i>

<i><small>max</small></i>

<i> = 0,4) - N</i>

<i><small>ev</small></i>

<i> = </i>

¹

<small>0,95</small>

<i> .ሾ19760 .0,0372 .63,9 + 0,18 .1,8 .ሺ63,9ሻ</i>

<small>3</small>

<i>ሿ= 138458,2 (W) - So the engine power under the motion resistance condition is: </i>

N

ev

= 138,458 (kW)

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IV. Xây dựng đường đặc tính ngồi của động cơ

- <i>Maximum engine power: </i>

(2.2) ⇒ N

<small>emax</small>

= 138,458 (kW)

- <i>Developing external speed characteristic curve: </i>

- <i>Determining the engine power at diffirent rotational speeds (using the Laydecman formula) </i>

(2.1) ⇒ N

<small>e</small>

= (N

<small>e</small>

)

<small>max</small>

.ሾ𝑎.λ + 𝑏 .λ

<small>2</small>

− 𝑐.λ

³

ሿ (kW) Where:

- <i>N<small>emax</small> and w<small>emax </small>represents the maximum power of the engine and the corresponding speed </i>

- <i>N<small>e</small> and w<small>e </small>represents the power and speed at a specific point on the characteristic curve </i>

- <i>Calculating the torque of the engine crankshaft at different speeds (RPMs) </i>

<i>o The parameters w<small>e</small>, N<small>e</small>, M<small>e</small> have their calculation formulas </i>

<i>o The calculated results are recorded in the table </i>

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IV.Xây dựng đường đặc tính ngoài của động cơ

Table 1: the table shows the engine torque and power

241,76103,80 108,

39

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<b>Development of the engine’s external speed characteristics</b>

After performing calculations and data processing, we have developed the external speed characteristic curve with engine power N

<small>e</small>

(kW) and torque M

<small>e </small>

(Nm):

Firgue 1: External speed characteristic curve graph of the engine

External speed characteristic curve

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<b>Development of the engine’s external speed characteristics</b>

<small>- </small> <i><small>Comments: </small></i>

<small>- </small> <i><small>The maximum Me value is determined according to the Laydecman formula as follows: </small></i>

Starting from the formula

𝑤_𝑒𝑁 ^{൤ 𝑏 ∗}1

𝑤_𝑒𝑁 ^{− 2𝑐 ∗}𝑤_𝑒

𝑤_𝑒𝑁<small>2</small>൨⇒ ^𝑤^𝑒𝑤_𝑒𝑁 ⁼

2𝑐 ^{= 0,5}⇒ M<small>emax</small>= ^𝑁<small>𝑒𝑚𝑎𝑥</small>

<small>𝑤</small>_𝑒𝑁 ቀ𝑎 +^𝑏²

<small>4 𝑐</small>ቁ = ^{13845 8 ,2}

<small>6 28</small> ቀ1 +¹²

<small>4</small>ቁ = 275,59 (Nm)

overcome motion resistance. To select an engine for an automobile, additional power is needed to overcome additional resistances such as fans, air compressors,...Therefore, the maximum power must be chosen

N<small>emax</small> = 1,1∗N<small>emax</small> = 1,1*262,81 = 289,09 (Nm)

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IV.Tính tốn các thơng số động lực học ơ tơ

-_{Transmission ratio of the power transmission system:}

i

_tl

= i

₀

. i

_h

. i

_c

. i

_p

(2.6)Where:

i

_tl

– transmission ratio of the power transmission systemi

₀

– transmission ratio of the main power transmissioni

_h

– transmission ratio of the gearbox

i

_c

– transmission ratio of the final power transmissioni

_p

– transmission ratio of the auxiliary gearbox

Typically i

_c

= 1; i

_p

= 1

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IV.Tính tốn các thơng số động lực học ơ tô

This is determined to ensure the car operates at its highest speed in the top gear of the gearbox-_{We have the equation:}

 

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IV.Tính tốn các thơng số động lực học ô tô

-Transmission ratio of gear 1:

The transmission of gear 1 is determined to ensure the car can overcome maximum road resistance without wheel slip under all driving conditions

Under driving conditions, we have:P

_{k max}

P

_{ψ max}

+ P

_w

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IV.Tính tốn các thơng số động lực học ô tô

- When the vehicle is operating in first gear, the speed is low. This allow us to disregard the air resistance force P

_w

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IV.Tính tốn các thông số động lực học ô tô

- Where:

G

_φ

– Load acting on the driving axle

φ – Coefficent of the road adhesion (φ = 0,7)r

_bx

– Average working radius of the wheels = 3,22

i

_h1

= 3,0718

 

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IV.Tính tốn các thơng số động lực học ơ tô

-_{The transmission ratio of the gear stages in the gear box is chosen according to the ‘geometric progression’}principle

-The multiplication factor is determined by the equation:

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IV.Tính tốn các thơng số động lực học ô tô

-The transmission ratio of the i-th gear stage in the gearbox is determined by the following formula:

i

_hi

– Transmission ratio of the i-th gear stage in the gearbox (i = 1; 2;…; n-1) -With these formulas, we can determine the transmission ratio of each gear stage:Transmission ratio of gear stage 2: i

_h2

= = = 2,4542

Transmission ratio of gear stage 3: i

_h3

= = = 1,9608Transmission ratio of gear stage 4: i

_h4

= = = 1,5666Transmission ratio of gear stage 5: i

_h5

= = = 1,2516Transmission ratio of gear stage 6: i

_h6

= = = 1

-Reverse transmission ratio: i

_e

= 1,2 i

_h1

= 1,23,0718 = 3,686

Verify the reverse transmission ratio according to the traction condition:

 

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IV.Tính tốn các thơng số động lực học ô tô

The transmission ratios corresponding to each gear are shown in the table below:

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IV.Tính tốn các thơng số động lực học ơ tơ

-The equation for the vehicle’s traction force balance:

P

_k

= P

_f

+ P

_i

+ P

_j

+ P

_w

(2.11)Where:

P

_k

– Traction force of the vehicleP

_k

=

P

_f

– Rolling resistance force: P

_f

= G.f = G.fP

_i

– Hill climbing resistance force: P

_i

= G = 0

P

_j

– Inertial force (occurs when the vehicle is in unstable motionP

_j

= j

P

_w

– Air resistance force: P

_w

= K.F.v

<small>2</small>

 

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-Speed correspoding to each gear:

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IV.Tính tốn các thơng số động lực học ơ tơ

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IV.Tính tốn các thơng số động lực học ơ tơ

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IV.Tính tốn các thơng số động lực học ô tô

-_{Equation for drag force balance Pc:}P

_c

= P

_f

+ P

_w

Considering a vehicle moving on a level road without windP

_c

= G.f + K.F.v²

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IV.Tính tốn các thơng số động lực học ô tô

Create a table to calculate P

_c

and Pφ:

-Plot the graph P

_k

=f(v) and P=f(v):

Figure 2: Traction force balance and speed for each gear

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IV.Tính tốn các thơng số động lực học ơ tơ

The vertical axis represents P

_k

, P

_f

, P

_w

, Pφ. The horizontal axis represents v (m/s)

The form of the car’s traction force graph P

_ki

= f(v) is similar to the curve M

_e

= f(n

_e

) of the external speed characteristic curve of the engine

The range between the traction force curve P

_ki

and the total traction force curve is the surplus traction force (P

_kd

) used for acceleration or climbing

The total traction force of the car must be less than the adhesion between the wheels and the road surface

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IV.Tính tốn các thơng số động lực học ơ tơ

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IV.Tính tốn các thơng số động lực học ơ tơ

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IV.Tính tốn các thông số động lực học ô tô

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IV.Tính tốn các thơng số động lực học ơ tơ

On the graph N

_k

= f(v), plot the graph according to the table -Consider a car moving on a level road:

N

_c

= G.f.v +K.F.v3(2.14)-Create a table to calculate :

Table 5: Powertrain resistance per transmission ratio

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Figure 3: Power balance graph of the car

VII.Tính tốn các thơng số động lực học ơ tơ

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IV.Tính tốn các thông số động lực học ô tô

The dynamics factor is the ratio between the difference of the traction force P_k and the air resistance P_w with the total weight of the car. This ratio is denoted as "D"

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IV.Tính tốn các thơng số động lực học ơ tơ

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IV.Tính tốn các thơng số động lực học ơ tơ

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IV.Tính tốn các thơng số động lực học ơ tơ

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V<b>. </b>Lập bảng tính giá trị thời gian tăng tốc – quãng đường tăng tốc của ôtô

-_{Dynamic factor under adhesion conditions is determined as}

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<b>V. Lập bảng tính giá trị thời gian tăng tốc – </b>

quãng đường tăng tốc của ôtô

Based on the table calculation results, construct the dynamic factor graph:

Figure 4: Dynamic factor graph of the vehicle

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V.Lập bảng tính giá trị thời gian tăng tốc – quãng đường tăng tốc của ôtô

The maximum value of the dynamic factor D

₁

max at the lowest transmission ratio represents the vehicle’s ability to overcome the largest driving resistance of the road: D

₁

max = 

_max

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V.Lập bảng tính giá trị thời gian tăng tốc – quãng đường tăng tốc của ôtô

-No-slip driving region of the vehicle:

Similar to traction force, the dynamic factor is also limited by the adhesion conditions of the drive wheels on the road surface. To prevent the vehicle from slipping during rotation, the dynamic factor D must satisfy the following condition:  ≤ D ≤ D

_φ

The region bounded by the D

_φ

curve and the  curve on the dynamic factor graph is the region that meets the above condition. When D > D

_φ

within a certain limit, the local characteristic of the engine can be used to prevent wheel slipping if practical operational conditions occur

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VII.Đánh gía khả năng kéo móc và vượt dốc

-Formula for calculating acceleration when the vehicle is moving on a level road:

J

_i

= .g (2.17)Where:

Di is the value of the dynamic factor at transmission ratio i, corresponding to the speed vi from the D = f(v) graph

f is the cofficient of rolling resistance

Ji is the acceleration of the vehicle in transmission ratio iis a factor considering the influence of rotating masses

= 1+0.05(1+i

_hi

²) (2.18)

 

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IV.Tính tốn các thơng số động lực học ơ tơ

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IV.Tính tốn các thơng số động lực học ơ tơ

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IV.Tính tốn các thơng số động lực học ô tô

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Based on the table calculation results, construct the acceleration graph:

Figure 5: Acceleration graph

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<i><b>Constructing the inverted acceleration graph:</b></i>

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Based on the table calculation results, construct the inverted acceleration graph:

Figure 6: Inverted acceleration graph

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<i><b>Calculate acceleration time and acceleration distance for a vehicle</b></i>

- <i><b>Acceleration time: </b></i>

<i><small>vv v</small></i>

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<i><b>Create a table to calculate the values of acceleration time and acceleration distance for the vehicle:</b></i>

-Consider speed loss and time during gear shifts

-Speed loss during gear shifts depends on the driver's skill level, gearbox structure, and engine type in the car

-_{Gasoline engines, with skilled drivers, have gear shift times ranging from 0.5s to 2s}-Calculate the speed loss during gear shifts:

Δ

_v

= (m/s) Where:

f

₀

- the cofficient of rolling resistancecs – acceleration time (tcs = 1s)

Δ

_v2

= 0,157471 (m/s)Δ

_v3

= 0,204382 (m/s)

Δ

_v4

= 0,275517 (m/s)Δ

_v5

= 0,393684 (m/s) Δ

_v6

= 0,589652 (m/s)

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-Create a table to calculate acceleration time and acceleration distance for a vehicle:

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<i><b>Accerelation time and distance graph of the vehicle</b></i>

Figure 7: Accerelation time and distance graph of the vehicle

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Calculating the traction dynamics of a car is only meaningful in theory due to the relative nature of the calculations and the inaccuracies in choosing coefficients during the computation compared to reality. In practice, evaluating the traction quality of a car is conducted on the road or on specialized testing benches

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