# Shifting Control Algorithm for a Single-Axle Parallel Plug-In Hybrid Electric Bus Equipped with EMT

Authors: Yunyun Yang; Sen Wu; Xiang Fu
Journal: Discrete Dynamics in Nature and Society
 (2014)

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## Abstract

Combining the characteristics of motor with fast response speed, an electric-drive automated mechanical transmission (EMT) is proposed as a novel type of transmission in this paper. Replacing the friction synchronization shifting of automated manual transmission (AMT) in HEVs, the EMT can achieve active synchronization of speed shifting. The dynamic model of a single-axle parallel PHEV equipped with the EMT is built up, and the dynamic properties of the gearshift process are also described. In addition, the control algorithm is developed to improve the shifting quality of the PHEV equipped with the EMT in all its evaluation indexes. The key techniques of changing the driving force gradient in preshifting and shifting compensation phases as well as of predicting the meshing speed in the gear meshing phase are also proposed. Results of simulation, bench test, and real road test demonstrate that the proposed control algorithm can reduce the gearshift jerk and the power interruption time noticeably.


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## Body

## 1. Introduction

In the past few years, hybrid electric vehicles (HEVs) have demonstrated advantages in reducing the fuel consumption and pollution emissions [1–3]. Compared with conventional HEVs, plug-in hybrid electric vehicles (PHEVs) can recharge from an external source. Before the technology of pure electric vehicles (EV) becomes mature, PHEVs offer a feasible solution to the transportation in which part of the required petroleum resource is replaced with electricity [4].The driveline system plays a crucial role in vehicle’s fuel-saving performance and driving comfort. Automated manual transmission (AMT) has been a decent candidate for the power transmission of heavy HEVs for its high efficiency, low cost, and high reliability. Besides, AMT can be modified in the conventional transmissions. However, AMT has still some drawbacks of power interruption and shifting jerk in the gear shifting process. Furthermore, the excessive wears of the clutch disc and synchronizer affect the application of AMT in HEVs [5–7]. Much research has been conducted to find better solutions to AMTs’ shortcomings in HEVs. For reducing the power interruption time, Baraszu and Cikanek [8] proposed that the vehicles should be directly driven by motor during the gear shifting process in parallel HEVs equipped with AMT. Jo et al. [9] and Liao et al. [10] introduced a control strategy which controlled the torques and speeds of the engine and motor to reduce the synchronizing torque of AMTs’ synchronizer and clutch. So far few literatures on the gear shifting control strategies without disengaging the clutch for HEVs equipped with AMT have been reported [5, 11, 12]. But those disadvantages of AMT could not be thoroughly avoided due to the slow response of engine.In order to solve these problems, we designed a new automatic transmission, namely, electric-drive automated mechanical transmission (EMT), which improved the structure of AMT. By removing the synchronizer of AMT and adding the drive motor and the control system to it, the EMT was constructed. With the rapid response of the motor, it could control the speed and torque of the motor to achieve shifting synchronization in gear shifting process. Thus the acceleration steadiness and the degree of smoothness of the vehicle are achieved [13–17], and consequently the vehicle drivability is improved.In this paper, a gear shifting control algorithm is designed for a single-axle parallel PHEV equipped with EMT. To do this, the dynamic properties of the gearshift process are discussed, and then the dynamic model of the powertrain system is built up. The EMT is integrated to a plug-in hybrid electric bus (PHEB). To study the effectiveness of the proposed gearshift control algorithm, the bench test and real road test are performed. The results of the simulation and tests prove that the presented control algorithm can obtain an outstanding gear shifting quality.


## 2. The Architecture and Working Principle of the EMT in Single-Axle Parallel PHEB

The powertrain system configuration of the single-axle parallel PHEB with EMT is shown in Figure1. In electric mode the clutch is disengaged, while in other modes the clutch is engaged. Those components including the engine, the EMT, the clutch, and the electrical controller are all controlled by the vehicle control unit (VCU). The EMT without reverse gear has several forward gears and the vehicle can achieve reversing by the motor rotating reversely.Figure 1
Structure diagram of a parallel PHEB powertrain with EMT.The configuration of a 4-gear EMT proposed in this paper is depicted in Figure2. As shown in Figure 2, the EMT is composed of a motor, a mechanical transmission with three shafts, and a shift actuator. Instead of the synchronizer in traditional transmission, the EMT uses the gear clutch teeth to mesh and separate in the gear shifting process, which is helpful for reducing the axial size. In gear shifting process, the EMT can shift to the target gear by adjusting the speed of the transmission input shaft (also the motor shaft) during the speed synchronization phase.Figure 2
Configuration of the four-gear EMT.The gear shifting process of the PHEV with EMT is shown in Figure3. The schematic diagram displays the vehicle starting with the 2nd gear and upshifting to the 4th gear continuously. When the vehicle starts, the engine is in an idle state and the clutch is disengaged; the EMT shifts to the 2nd gear; and the vehicle runs in a pure electric mode. As the motor speed increases to the upshift point, the EMT switches to the 3rd gear. After gear shifting, the vehicle still runs in the electric mode; when the engine and the motor are controlled to have the same rotating speed, the clutch is engaged. The vehicle is driven solely by the motor during the whole clutch engagement process. After the clutch is engaged, the vehicle switches to the hybrid mode (decided by the whole vehicle energy management strategy). When the speeds of the engine and the motor increase to the 3rd upshift point, the clutch is separated and the transmission shifts off to the neutral gear, and then the EMT starts to switch to the 4th gear, which shares the same principle with the shift from the 2nd gear to the 3rd gear.Figure 3
Gear shifting process of the PHEV with EMT.


## 3. Gear Shifting Quality Evaluation Indexes

The gear shifting quality evaluation indexes of the PHEV with EMT are power interruption time, shifting jerk [18, 19], and the service life of the shifting components.


### 3.1. Power Interruption Time

The power interruption timetPI refers to the time when vehicle is decelerating in the gear shifting process, namely, the time when the acceleration is negative. The gear shifting time of the single-axle parallel HEV with EMT includes the time t1 of disengaging the clutch, the time t2 of shifting-off to the neutral gear, the time t3 of motor active synchronization, and the time t4 of shifting on the target gear. Then the equation of the power interruption time can be expressed as
(1)tPI=max⁡t1,t2+t3+t4.


### 3.2. Gear Shifting Jerk

The gear shifting jerk is the changing rate of the vehicle’s acceleration [20, 21]; it significantly influences the drivability during the shifting process and can be represented as
(2)j=dadt=ddtdvdt,
where v is the vehicle velocity; a is the vehicle longitudinal acceleration.


## 3.1. Power Interruption Time

The power interruption timetPI refers to the time when vehicle is decelerating in the gear shifting process, namely, the time when the acceleration is negative. The gear shifting time of the single-axle parallel HEV with EMT includes the time t1 of disengaging the clutch, the time t2 of shifting-off to the neutral gear, the time t3 of motor active synchronization, and the time t4 of shifting on the target gear. Then the equation of the power interruption time can be expressed as
(1)tPI=max⁡t1,t2+t3+t4.


## 3.2. Gear Shifting Jerk

The gear shifting jerk is the changing rate of the vehicle’s acceleration [20, 21]; it significantly influences the drivability during the shifting process and can be represented as
(2)j=dadt=ddtdvdt,
where v is the vehicle velocity; a is the vehicle longitudinal acceleration.


## 4. Control Algorithm Analyses for EMT Shifting

For obtaining excellent gear shifting quality, an optimal control algorithm is critical. When the vehicle is not in gear shifting process, the motor and engine are controlled by the VCU according to the vehicle control strategies and can be represented as follows:(3)Te=fαe,ne,Tm=Treq-Te,
where αe is the engine throttle opening, ne is the engine speed, Treq is the vehicle demand torque, Te is the output torque of the engine, and Tm is the output torque of the motor.The gear shifting process of the single-axial parallel PHEV with EMT is shown in Figure4. When the target gear is determined by the input conditions, the EMT switches to the shifting mode (step ① in Figure 4). The process starts with the preshifting procedure (step ② in Figure 4) determined by the torque request of the vehicle, which can make the vehicle transit to the shifting operating procedure smoothly. Then the EMT evaluates the target gear in real time according to the road condition and driver’s physical conditionbecause the preshifting phase has no power interruption (step ③ in Figure 4). When the target gear is confirmed, the EMT switches to the gear shifting operation procedure (the key of gearshift process). After shifting to the target gear, the EMT starts the shifting compensation procedure (step ④ in Figure 4), which compensates the torque request for the vehicle. With the finish of the phase ④, the shifting mode ends and is followed by the driver operating mode (step ⑤ in Figure 4). In the synthesis, the gear shifting process in a single-axle parallel PHEV with EMT is divided into five processes, forming the whole power process of driving and shifting. The concrete analysis of the gear shifting processes ②   ③   ④ will be done below.Figure 4
Flow diagram of the gearshift process for the PHEV equipped with EMT.


### 4.1. Preshifting Process

When the vehicle needs to shift to the new gear which is determined by the VCU, the powertrain switches to the shifting mode and starts the preshifting program. The system breaks off the shifting program only when the brake pedal is stamped by the driver. And then the system responds to the control strategies of the vehicle and gear shifting; otherwise the system switches to the shifting process smoothly. The main function of the preshifting program is to weaken the negative effects of the power interruption in the shifting process.When the vehicle is running on a flat road, the driving force can be expressed as(4)Ft=Ff+Fw+Fj,
where Ft is the driving force, Ff is the rolling resistance, Fw is the air resistance, and Fj is the acceleration resistance which is related to the acceleration. The equation of Fj can be expressed as follows:
(5)Fj=δ1mdudt,
where m is the gross vehicle weight and δ1 is the rotary mass coefficient of the vehicle in this process. The equation of the shifting jerk can be represented as
(6)j=d2udt2=dFj/δmdt=dFt-Ff-Fwδmdt.According to the shifting requirements, the shifting jerk must meet the following condition:(7)j≤jmax⁡,
where jmax⁡ is the reference value of the maximum gear shifting jerk. The recommended values are 31.63 m/s3 in former Soviet Union and 10 m/s3 in Germany.To avoid the power interruption in the preshifting phase and to minimize the shifting jerk of the switching to neutral gear in the shifting process, the vehicle acceleration in the end of the preshifting phase should approach zero, and thus the equation can be written as follows:(8)Fw1+Ff1-Ft1=0,
where Fw1, Ff1, and Ft1 are the air resistance, the rolling resistance, and the driving force in the end of the preshifting phase.Then the equation of average jerkja is
(9)ja=Ft1-Fw1-Ff1-Ft0-Fw0-Ff0δ1mΔt01=Fw0+Ff0-Ft0δ1mΔt01≤jmax⁡,
where Fw0, Ff0, and Ft0 are the air resistance, the rolling resistance, and the driving force in the beginning of the preshifting phase and Δt01 is the time of the preshifting phase.From (8) and (9), we can get
(10)Ft0Δt01≥Fw0+Ff0Δt01-δ1mjmax⁡.The shifting jerk of the preshifting process can be ensured to meet (7) by controlling the driving force gradient (dFt/dt) with the following requirement:
(11)dFtdt≥Fw0+Ff0Δt01-δ1mjmax⁡.In the preshifting phase, the output torque of the power source (decided by the vehicle control strategies) is controlled by the control strategy of the driving force gradient.


### 4.2. Shifting Operation Process

The shifting operation process has three phases: shifting-off phase, motor active speed synchronization phase, and shifting compensation phase. The following actions will be performed to realize the shifting.(a)
Disengage the clutch in the shortest time according to the indexes of the shifting jerk and the power interruption time; meanwhile, the motor switches to the idle mode with no torque output and the engine switches to the idle mode. Then the transmission switches to the neutral gear.(b)
In order to realize the speed synchronization of the input and output shafts, the motor adjusts the speed in torque control mode; meanwhile, the target speed of the motor is calculated.(c)
The transmission switches to the target gear when it meets the shifting requirements.


#### 4.2.1. Shifting-Off Phase

In this phase, the clutch starts to separate and the transmission switches to the neutral gear. The average jerk of this phase can be represented as(12)ja1=Ft2-Fw2-Ff2/δ2m-Ft1-Fw1-Ff1/δ1mΔt12,
where Fw2, Ff2, and Ft2 are the air resistance, the rolling resistance, and the driving force in the end of the shifting-off phase, Δt12 is the time of the shifting-off phase, and ja1 is the average jerk of this phase.In the gearshift process, we may consider that the vehicle acceleration is approximately equal to zero, so it is easy to shift off without excessive wear on the gears surfaces. Then the rolling resistance and the air resistance keep unchanged. The average jerk can also be represented as(13)ja1=-Fw2+Ff2δ2mΔt12=-Fw1+Ff1δ1mΔt12=-Fw0+Ff0δ1mΔt12.


#### 4.2.2. Motor Active Speed Synchronization Phase

After switching to the neutral gear, start to reduce the speed difference between the shift sleeve and shift gear of the target gear, which is called motor active speed synchronization phase.The sketch of the movement positions of the shift sleeve teeth in shifting process is shown in Figure5. The red teeth represent the teeth of the shift sleeve while the blue ones represent those ofthe shift gear. A stands for the end of the active synchronization phase and B stands for the beginning of the gear meshing; C stands for the end of the gear meshing; ω1A, ω1B, and ω1C represent the rotating speed of the shift sleeve in stages A, B, and C, respectively; ω2A, ω2B, and ω2C represent the speed of theshift gear in stages A, B, and C, respectively.Figure 5
The movement positions of the shift sleeve in shifting process.The speeds of the input shaft and the output shaft should be predicted in the process fromA to B, which is the idle motion process of the shift sleeve. The ideal condition of B is
(14)ω1B=ω2B.In the active speed synchronization phase, the speed variation trends of the shift sleeve and shift gear should be predicted accurately. By theoretical analysis, this paper adopts the mean evaluation method to predict the target speed of the speed regulation. The equations of this phase are as follows:(15)ω1B=ω1A+a1·tA-B,ω2B=ω2A+a2·tA-B,ω1A+a1·tA-B=ω2A+a2·tA-B,
where a1 is the acceleration of the shiftsleeve, a2 is the acceleration of the gear shaft, and tA-B is the time from A to B.The speed of shift sleeveis measured by the speed sensor of the output shaft, while the speed of gear shaft is measured by the speed sensor of the motor;a1 is calculated by the relationship between the speed of the output shaft and the speed regulation time. At the end of the active synchronization phase, the acceleration of the motor cannot be measured, so the acceleration of the gear shaft a2 cannot be obtained either. Through numerous experiments, the value of ω2B can be predicted as follows:
(16)ω2A+a2·tA-B=kp·ω2A,
where kp is the proportionality coefficient which is related to the speed and the output torque of the motor. In practical applications, the parameter compensations are added to the output shaft acceleration a1 which is replaced with the weight value Σa1. The equation of the weight value Σa1 can be expressed as(17)Σa1=ka1+1-kaa,
where k is the weight coefficient which is related to the vehicle speed in the beginning of the active synchronization and aa is the average speed of shift sleeve in the active synchronization. Then ω2A can be controlled as the following equation:
(18)ω2A=ω1A+Σa1·tA-Bkp.


#### 4.2.3. Gear Meshing Phase

In this phase, the teeth of shift sleeve and those of shift gear begin to mesh. As shown in Figure6, there are four different position relationships between the teeth of shift sleeve and those of shift gear in the gear meshing phase. The stages 2 and 4 are both special situations, representing small probability events, while the stages 1 and 3 appear in most cases. Although the causes of stages 1 and 3 are different, they have the same force situation. Take stage 1, for example, to analyze the force of the meshing teeth at the contact moment.Figure 6
Position relationships between the teeth of shift sleeve and those of shift gear.The acting forces applied on the tooth of shift sleeve and those on the shift gear are shown in Figure7. The equations of the forces can be expressed as follows:
(19)Ms=Ft×ds2,(20)Ft=Ft1-Ft2,(21)FR=us×FN,(22)Fa=Fa′′+Fa′,(23)Ft=FNcos⁡β2-us×sinβ2,(24)Fa=FNsinβ2+us×cos⁡β2,(25)FN=Fasinβ/2+us×cos⁡β/2,(26)Ft=Facos⁡β/2-us×sinβ/2sinβ/2+us×cos⁡β/2,(27)Ms=Fa×dscos⁡β/2-us×sinβ/22sinβ/2+us×cos⁡β/2,(28)Mk=Jt·dω2dt,
where Ms is the blocking torque, Ft is the tangential (along circumferential direction) force component, FR is the frictional force, FN is the normal force, Fa is the axial shift force, da is the mean effective diameter of the shift gear, β is the angle of roof shape of the shift gear tooth, us is the static friction coefficient of gear’s meshing surface, Mk is the moment of inertia, Jt is the equivalent rotational inertia of jackshaft and the gears thereon, and ω2 is the rotational speed of the shift gear.Figure 7
The acting forces applied on the tooth of shift sleeve and those on the shift gear.The axial forceFk is generated by the moment of inertia Mk which can be expressed as
(29)Fk=Mkds/2cotβ.The teeth of shift sleeve and those of shift gear can mesh without failure when the following two conditions are satisfied: (1)Fk<Fa; (2) Mk<Ma.To simplify the modeling, the static friction coefficientus is assumed to be zero, so (27) can be simplified as follows:
(30)Ms=Fa×ds2cotβ2.AsMk<Ma, we can get
(31)Fa>Jds/2·dωdttanβ2.In this phase, the shifting jerkj3 can be represented as
(32)j3=ddtdudt=ddti0ηδ3mrMk=i0ηδ3mrdMkdt≤jmax⁡,
where m is the gross vehicle weight, δ3 is the rotary mass coefficient of the vehicle in the target gear, η is the mechanical efficiency of transmission system, and i0 is the main reduction ratio.The maximum shifting jerk occurs at the moment when the teeth of shift gear contact those of the shift sleeve. According to (32), we know that the gear shifting jerk is connected with the change of the synthetic speed difference.


### 4.3. Shifting Compensation Phase

After shifting, the output torque of the motor is restored and the vehicle is driven by the motor. In this phase, the same control algorithm as that in the preshifting process is used to restore the output torque of the motor. The driving force gradient (dFt/dt) equation is expressed as
(33)dFtdt=Ft5t45≤jmax⁡·δ3m,
where Ft5 is the air resistance in the end of the shifting compensation phase and Δt45 is the time of this phase.In hybrid mode and engine mode, the clutch is engaged after this phase. Then the vehicle comes back to the driving mode which is controlled by the vehicle control strategies.


## 4.1. Preshifting Process

When the vehicle needs to shift to the new gear which is determined by the VCU, the powertrain switches to the shifting mode and starts the preshifting program. The system breaks off the shifting program only when the brake pedal is stamped by the driver. And then the system responds to the control strategies of the vehicle and gear shifting; otherwise the system switches to the shifting process smoothly. The main function of the preshifting program is to weaken the negative effects of the power interruption in the shifting process.When the vehicle is running on a flat road, the driving force can be expressed as(4)Ft=Ff+Fw+Fj,
where Ft is the driving force, Ff is the rolling resistance, Fw is the air resistance, and Fj is the acceleration resistance which is related to the acceleration. The equation of Fj can be expressed as follows:
(5)Fj=δ1mdudt,
where m is the gross vehicle weight and δ1 is the rotary mass coefficient of the vehicle in this process. The equation of the shifting jerk can be represented as
(6)j=d2udt2=dFj/δmdt=dFt-Ff-Fwδmdt.According to the shifting requirements, the shifting jerk must meet the following condition:(7)j≤jmax⁡,
where jmax⁡ is the reference value of the maximum gear shifting jerk. The recommended values are 31.63 m/s3 in former Soviet Union and 10 m/s3 in Germany.To avoid the power interruption in the preshifting phase and to minimize the shifting jerk of the switching to neutral gear in the shifting process, the vehicle acceleration in the end of the preshifting phase should approach zero, and thus the equation can be written as follows:(8)Fw1+Ff1-Ft1=0,
where Fw1, Ff1, and Ft1 are the air resistance, the rolling resistance, and the driving force in the end of the preshifting phase.Then the equation of average jerkja is
(9)ja=Ft1-Fw1-Ff1-Ft0-Fw0-Ff0δ1mΔt01=Fw0+Ff0-Ft0δ1mΔt01≤jmax⁡,
where Fw0, Ff0, and Ft0 are the air resistance, the rolling resistance, and the driving force in the beginning of the preshifting phase and Δt01 is the time of the preshifting phase.From (8) and (9), we can get
(10)Ft0Δt01≥Fw0+Ff0Δt01-δ1mjmax⁡.The shifting jerk of the preshifting process can be ensured to meet (7) by controlling the driving force gradient (dFt/dt) with the following requirement:
(11)dFtdt≥Fw0+Ff0Δt01-δ1mjmax⁡.In the preshifting phase, the output torque of the power source (decided by the vehicle control strategies) is controlled by the control strategy of the driving force gradient.


## 4.2. Shifting Operation Process

The shifting operation process has three phases: shifting-off phase, motor active speed synchronization phase, and shifting compensation phase. The following actions will be performed to realize the shifting.(a)
Disengage the clutch in the shortest time according to the indexes of the shifting jerk and the power interruption time; meanwhile, the motor switches to the idle mode with no torque output and the engine switches to the idle mode. Then the transmission switches to the neutral gear.(b)
In order to realize the speed synchronization of the input and output shafts, the motor adjusts the speed in torque control mode; meanwhile, the target speed of the motor is calculated.(c)
The transmission switches to the target gear when it meets the shifting requirements.


### 4.2.1. Shifting-Off Phase

In this phase, the clutch starts to separate and the transmission switches to the neutral gear. The average jerk of this phase can be represented as(12)ja1=Ft2-Fw2-Ff2/δ2m-Ft1-Fw1-Ff1/δ1mΔt12,
where Fw2, Ff2, and Ft2 are the air resistance, the rolling resistance, and the driving force in the end of the shifting-off phase, Δt12 is the time of the shifting-off phase, and ja1 is the average jerk of this phase.In the gearshift process, we may consider that the vehicle acceleration is approximately equal to zero, so it is easy to shift off without excessive wear on the gears surfaces. Then the rolling resistance and the air resistance keep unchanged. The average jerk can also be represented as(13)ja1=-Fw2+Ff2δ2mΔt12=-Fw1+Ff1δ1mΔt12=-Fw0+Ff0δ1mΔt12.


### 4.2.2. Motor Active Speed Synchronization Phase

After switching to the neutral gear, start to reduce the speed difference between the shift sleeve and shift gear of the target gear, which is called motor active speed synchronization phase.The sketch of the movement positions of the shift sleeve teeth in shifting process is shown in Figure5. The red teeth represent the teeth of the shift sleeve while the blue ones represent those ofthe shift gear. A stands for the end of the active synchronization phase and B stands for the beginning of the gear meshing; C stands for the end of the gear meshing; ω1A, ω1B, and ω1C represent the rotating speed of the shift sleeve in stages A, B, and C, respectively; ω2A, ω2B, and ω2C represent the speed of theshift gear in stages A, B, and C, respectively.Figure 5
The movement positions of the shift sleeve in shifting process.The speeds of the input shaft and the output shaft should be predicted in the process fromA to B, which is the idle motion process of the shift sleeve. The ideal condition of B is
(14)ω1B=ω2B.In the active speed synchronization phase, the speed variation trends of the shift sleeve and shift gear should be predicted accurately. By theoretical analysis, this paper adopts the mean evaluation method to predict the target speed of the speed regulation. The equations of this phase are as follows:(15)ω1B=ω1A+a1·tA-B,ω2B=ω2A+a2·tA-B,ω1A+a1·tA-B=ω2A+a2·tA-B,
where a1 is the acceleration of the shiftsleeve, a2 is the acceleration of the gear shaft, and tA-B is the time from A to B.The speed of shift sleeveis measured by the speed sensor of the output shaft, while the speed of gear shaft is measured by the speed sensor of the motor;a1 is calculated by the relationship between the speed of the output shaft and the speed regulation time. At the end of the active synchronization phase, the acceleration of the motor cannot be measured, so the acceleration of the gear shaft a2 cannot be obtained either. Through numerous experiments, the value of ω2B can be predicted as follows:
(16)ω2A+a2·tA-B=kp·ω2A,
where kp is the proportionality coefficient which is related to the speed and the output torque of the motor. In practical applications, the parameter compensations are added to the output shaft acceleration a1 which is replaced with the weight value Σa1. The equation of the weight value Σa1 can be expressed as(17)Σa1=ka1+1-kaa,
where k is the weight coefficient which is related to the vehicle speed in the beginning of the active synchronization and aa is the average speed of shift sleeve in the active synchronization. Then ω2A can be controlled as the following equation:
(18)ω2A=ω1A+Σa1·tA-Bkp.


### 4.2.3. Gear Meshing Phase

In this phase, the teeth of shift sleeve and those of shift gear begin to mesh. As shown in Figure6, there are four different position relationships between the teeth of shift sleeve and those of shift gear in the gear meshing phase. The stages 2 and 4 are both special situations, representing small probability events, while the stages 1 and 3 appear in most cases. Although the causes of stages 1 and 3 are different, they have the same force situation. Take stage 1, for example, to analyze the force of the meshing teeth at the contact moment.Figure 6
Position relationships between the teeth of shift sleeve and those of shift gear.The acting forces applied on the tooth of shift sleeve and those on the shift gear are shown in Figure7. The equations of the forces can be expressed as follows:
(19)Ms=Ft×ds2,(20)Ft=Ft1-Ft2,(21)FR=us×FN,(22)Fa=Fa′′+Fa′,(23)Ft=FNcos⁡β2-us×sinβ2,(24)Fa=FNsinβ2+us×cos⁡β2,(25)FN=Fasinβ/2+us×cos⁡β/2,(26)Ft=Facos⁡β/2-us×sinβ/2sinβ/2+us×cos⁡β/2,(27)Ms=Fa×dscos⁡β/2-us×sinβ/22sinβ/2+us×cos⁡β/2,(28)Mk=Jt·dω2dt,
where Ms is the blocking torque, Ft is the tangential (along circumferential direction) force component, FR is the frictional force, FN is the normal force, Fa is the axial shift force, da is the mean effective diameter of the shift gear, β is the angle of roof shape of the shift gear tooth, us is the static friction coefficient of gear’s meshing surface, Mk is the moment of inertia, Jt is the equivalent rotational inertia of jackshaft and the gears thereon, and ω2 is the rotational speed of the shift gear.Figure 7
The acting forces applied on the tooth of shift sleeve and those on the shift gear.The axial forceFk is generated by the moment of inertia Mk which can be expressed as
(29)Fk=Mkds/2cotβ.The teeth of shift sleeve and those of shift gear can mesh without failure when the following two conditions are satisfied: (1)Fk<Fa; (2) Mk<Ma.To simplify the modeling, the static friction coefficientus is assumed to be zero, so (27) can be simplified as follows:
(30)Ms=Fa×ds2cotβ2.AsMk<Ma, we can get
(31)Fa>Jds/2·dωdttanβ2.In this phase, the shifting jerkj3 can be represented as
(32)j3=ddtdudt=ddti0ηδ3mrMk=i0ηδ3mrdMkdt≤jmax⁡,
where m is the gross vehicle weight, δ3 is the rotary mass coefficient of the vehicle in the target gear, η is the mechanical efficiency of transmission system, and i0 is the main reduction ratio.The maximum shifting jerk occurs at the moment when the teeth of shift gear contact those of the shift sleeve. According to (32), we know that the gear shifting jerk is connected with the change of the synthetic speed difference.


## 4.2.1. Shifting-Off Phase

In this phase, the clutch starts to separate and the transmission switches to the neutral gear. The average jerk of this phase can be represented as(12)ja1=Ft2-Fw2-Ff2/δ2m-Ft1-Fw1-Ff1/δ1mΔt12,
where Fw2, Ff2, and Ft2 are the air resistance, the rolling resistance, and the driving force in the end of the shifting-off phase, Δt12 is the time of the shifting-off phase, and ja1 is the average jerk of this phase.In the gearshift process, we may consider that the vehicle acceleration is approximately equal to zero, so it is easy to shift off without excessive wear on the gears surfaces. Then the rolling resistance and the air resistance keep unchanged. The average jerk can also be represented as(13)ja1=-Fw2+Ff2δ2mΔt12=-Fw1+Ff1δ1mΔt12=-Fw0+Ff0δ1mΔt12.


## 4.2.2. Motor Active Speed Synchronization Phase

After switching to the neutral gear, start to reduce the speed difference between the shift sleeve and shift gear of the target gear, which is called motor active speed synchronization phase.The sketch of the movement positions of the shift sleeve teeth in shifting process is shown in Figure5. The red teeth represent the teeth of the shift sleeve while the blue ones represent those ofthe shift gear. A stands for the end of the active synchronization phase and B stands for the beginning of the gear meshing; C stands for the end of the gear meshing; ω1A, ω1B, and ω1C represent the rotating speed of the shift sleeve in stages A, B, and C, respectively; ω2A, ω2B, and ω2C represent the speed of theshift gear in stages A, B, and C, respectively.Figure 5
The movement positions of the shift sleeve in shifting process.The speeds of the input shaft and the output shaft should be predicted in the process fromA to B, which is the idle motion process of the shift sleeve. The ideal condition of B is
(14)ω1B=ω2B.In the active speed synchronization phase, the speed variation trends of the shift sleeve and shift gear should be predicted accurately. By theoretical analysis, this paper adopts the mean evaluation method to predict the target speed of the speed regulation. The equations of this phase are as follows:(15)ω1B=ω1A+a1·tA-B,ω2B=ω2A+a2·tA-B,ω1A+a1·tA-B=ω2A+a2·tA-B,
where a1 is the acceleration of the shiftsleeve, a2 is the acceleration of the gear shaft, and tA-B is the time from A to B.The speed of shift sleeveis measured by the speed sensor of the output shaft, while the speed of gear shaft is measured by the speed sensor of the motor;a1 is calculated by the relationship between the speed of the output shaft and the speed regulation time. At the end of the active synchronization phase, the acceleration of the motor cannot be measured, so the acceleration of the gear shaft a2 cannot be obtained either. Through numerous experiments, the value of ω2B can be predicted as follows:
(16)ω2A+a2·tA-B=kp·ω2A,
where kp is the proportionality coefficient which is related to the speed and the output torque of the motor. In practical applications, the parameter compensations are added to the output shaft acceleration a1 which is replaced with the weight value Σa1. The equation of the weight value Σa1 can be expressed as(17)Σa1=ka1+1-kaa,
where k is the weight coefficient which is related to the vehicle speed in the beginning of the active synchronization and aa is the average speed of shift sleeve in the active synchronization. Then ω2A can be controlled as the following equation:
(18)ω2A=ω1A+Σa1·tA-Bkp.


## 4.2.3. Gear Meshing Phase

In this phase, the teeth of shift sleeve and those of shift gear begin to mesh. As shown in Figure6, there are four different position relationships between the teeth of shift sleeve and those of shift gear in the gear meshing phase. The stages 2 and 4 are both special situations, representing small probability events, while the stages 1 and 3 appear in most cases. Although the causes of stages 1 and 3 are different, they have the same force situation. Take stage 1, for example, to analyze the force of the meshing teeth at the contact moment.Figure 6
Position relationships between the teeth of shift sleeve and those of shift gear.The acting forces applied on the tooth of shift sleeve and those on the shift gear are shown in Figure7. The equations of the forces can be expressed as follows:
(19)Ms=Ft×ds2,(20)Ft=Ft1-Ft2,(21)FR=us×FN,(22)Fa=Fa′′+Fa′,(23)Ft=FNcos⁡β2-us×sinβ2,(24)Fa=FNsinβ2+us×cos⁡β2,(25)FN=Fasinβ/2+us×cos⁡β/2,(26)Ft=Facos⁡β/2-us×sinβ/2sinβ/2+us×cos⁡β/2,(27)Ms=Fa×dscos⁡β/2-us×sinβ/22sinβ/2+us×cos⁡β/2,(28)Mk=Jt·dω2dt,
where Ms is the blocking torque, Ft is the tangential (along circumferential direction) force component, FR is the frictional force, FN is the normal force, Fa is the axial shift force, da is the mean effective diameter of the shift gear, β is the angle of roof shape of the shift gear tooth, us is the static friction coefficient of gear’s meshing surface, Mk is the moment of inertia, Jt is the equivalent rotational inertia of jackshaft and the gears thereon, and ω2 is the rotational speed of the shift gear.Figure 7
The acting forces applied on the tooth of shift sleeve and those on the shift gear.The axial forceFk is generated by the moment of inertia Mk which can be expressed as
(29)Fk=Mkds/2cotβ.The teeth of shift sleeve and those of shift gear can mesh without failure when the following two conditions are satisfied: (1)Fk<Fa; (2) Mk<Ma.To simplify the modeling, the static friction coefficientus is assumed to be zero, so (27) can be simplified as follows:
(30)Ms=Fa×ds2cotβ2.AsMk<Ma, we can get
(31)Fa>Jds/2·dωdttanβ2.In this phase, the shifting jerkj3 can be represented as
(32)j3=ddtdudt=ddti0ηδ3mrMk=i0ηδ3mrdMkdt≤jmax⁡,
where m is the gross vehicle weight, δ3 is the rotary mass coefficient of the vehicle in the target gear, η is the mechanical efficiency of transmission system, and i0 is the main reduction ratio.The maximum shifting jerk occurs at the moment when the teeth of shift gear contact those of the shift sleeve. According to (32), we know that the gear shifting jerk is connected with the change of the synthetic speed difference.


## 4.3. Shifting Compensation Phase

After shifting, the output torque of the motor is restored and the vehicle is driven by the motor. In this phase, the same control algorithm as that in the preshifting process is used to restore the output torque of the motor. The driving force gradient (dFt/dt) equation is expressed as
(33)dFtdt=Ft5t45≤jmax⁡·δ3m,
where Ft5 is the air resistance in the end of the shifting compensation phase and Δt45 is the time of this phase.In hybrid mode and engine mode, the clutch is engaged after this phase. Then the vehicle comes back to the driving mode which is controlled by the vehicle control strategies.


## 5. Simulation Analysis

The gear shifting process of the hybrid electric drivetrain system is a sophisticated multi-rigid-body control system with complicated physical properties. So it is difficult to get the accurate shifting performance. Then let us analyze the control algorithm proposed above with the virtual prototype technology. The EMT model is simulated on the software ADAMS (Automatic Dynamic Analysis of Mechanical Systems). For simplifying the simulation model, the 4-speed EMT is replaced with a 2-speed EMT mode as shown in Figure8.Figure 8
The EMT gear shifting process simulation.The simulation results of the speed and the shifting fork displacement response in the upshift process are shown in Figure9. The EMT shifting control algorithm can satisfactorily meet the gearshift requirements. In the process of shifting from the 1st to the 2nd gear and when the speed of the input shaft is adjusted to approach the output shaft speed, the shifting fork starts moving, and the transmission shifts to the 2nd gear. During the whole gear shifting process, the speed fluctuation of each shaft is small and so is the shifting jerk.Figure 9
Simulation results of EMT shifting process.By optimizing the simulation parameters, we can get various shifting results of different motor torques in speed synchronization phase, as shown in Table1; the sampling frequency is 25 ms. The power interruption time is no more than 0.85 s. We can also notice that the greater the torque of the motor regulating speed is, the shorter the power interrupt time is; and also the shorter the power interrupt time is, the greater the shifting jerk will be. When the torque of the regulating speed is below the 100%, the power interruption time reduces with the increase of it, while when the torque of the regulating speed is over 100%, the power interruption time change is small. This is due to the fact that, with the increase of the torque of the motor speed adjustment, the gear meshing time is longer despite the fact that the shifting-off time and motor active synchronization time are shorter. According to the simulation results, we also know that, with the shifting control algorithm, the shifting jerk has been decreased and the shifting quality has been improved.Table 1
Simulation results of shifting quality with different motor torques.
Torque of the motor speed adjustment/%
Shifting-off time/ms
Motor active synchronization time/ms
Gear meshing time/ms
Power  interruption  time/ms
Shifting jerk/m/s3
t
2
t
3
t
4
t
J
40
150
625
75
850
6.9
60
150
400
75
625
7.8
80
150
325
75
550
8.2
100
150
250
75
475
9.6
150
125
200
150
475
15.6


## 6. Bench Test and Road Test

To verify the control algorithm for shifting a single-axle parallel PHEB equipped with EMT, the bench test and road test were conducted, respectively. The vehicle parameters are shown in Table2. The shifting process control model is shown in Figure 10. The test bench picture is shown in Figure 11.Table 2
The powertrain and vehicle parameters of the PHEB.
Parameters
Value
Curb weight/full load gross mass/kg
13000/18000
Main reducer ratio
6.2
Transmission ration (4-gear)
5.82; 3.23; 1.79; 1
Engine displacement/L
2.98
Maximum power (kW)/speed (rpm)
95/3200
Maximum torque (Nm)/speed (rpm)
345/1600~2400
Motor
Induction motor
Rated/peak power (kW)
80/160
Maximum torque (N·m)
954
Lithium ion battery
Capacitor (Ah)/rated voltage (V)
160/576Figure 10
The diagram of the shifting process control model.Figure 11
The test bench.The control system of the dynamometer can display the output torque and speed of power sources in real time, and the shifting jerk of output shaft can be calculated simultaneously. The test results of the continuous upshift and downshift processes performed with the EMT in the bench test are shown in Figure12. For analyzing the control algorithm, the test results of the output shaft speed and the input shaft speed are shown in Figure 13 with marks. As shown in Figure 13, the phases of BC (1st to 2nd), DE (2nd to 3rd), and FG (3rd to 4th) are the upshift processes, while those of IJ (4th to 3rd), KL (3rd to 2nd), and MN (2nd to 1st) are the downshift processes.Figure 12
Test results of shifting process.Figure 13
Test results of shifting with marks.The bench test results of shifting jerk are shown in Figure14. The results of power interrupting time and shifting jerk of each gear are shown in Table 3. As can be seen from the Table, the power interrupt time is controlled within 0.85 s, and the shifting jerk is controlled within 8.6 m/s3. The motor active synchronization phase takes about 70% of the power interrupt time, which is impacted by the torque of the motor speed adjustment.Table 3
The statistical data of the gearshift quality.
Gear change
t
2/s
t
3/s
t
4/s
t
PI/s
Maximum shifting jerk m/s3
1→2
0.12
0.53
0.11
0.76
5.2
2→3
0.10
0.61
0.10
0.81
8.1
3→4
0.09
0.64
0.12
0.85
8.6
4→3
0.09
0.46
0.10
0.65
-
3.9
3→2
0.09
0.50
0.14
0.73
-
3.2
2→1
0.10
0.45
0.13
0.68
-
4.7Figure 14
The test results of shifting jerk.After plenty of bench tests, the road tests with a 12 m PHEV equipped with the EMT were conducted. The picture of the PHEB is shown in Figure15. According to the control strategies, the test results of the engine speed, gear position sensor signals, clutch position sensor signals, motor speed, output shaft speed, and speed ratios are shown in Figure 16. The curves show the test processes in which the PHEB was starting with the 2nd gear and accelerating to the 4th gear and then decelerating and downshifting to the 2nd gear. The power interrupt time of the PHEB is less than 0.8 s, and the speed of the output shaft changes smoothly. The shifting jerk is no more than 10 m/s3 which meets the recommended reference value of the shifting jerk in Germany.Figure 15
The test PHEB with EMT.Figure 16
Road test curves of the gear shifting.


## 7. Conclusions

In this paper, the working principle of a single-axle parallel PHEV equipped with an EMT is described, and analysis of the shifting dynamics model in each transient process is also given in detail. Moreover, a new shifting control algorithm is introduced for improving the gearshift quality without synchronizer. With the control algorithm, the gears of the single-axle parallel PHEV equipped with the EMT can be controlled to engage faster and successfully without excessive wear on the gear surfaces. It is also important to note that the control algorithm was verified on a simulation platform by the bench test and PHEB test. All the results prove that adopting this control algorithm in parallel PHEV equipped with the EMT can improve the shifting quality significantly through its evaluation indexes, which is likely to help to replace the traditional AMT in HEV.The EMT with proposed shifting control algorithm can also be applied to EVs and other kinds of HEVs to improve the shifting quality. In the near future, further study on EMT shifting will be carried on, and the new shifting algorithm will be proposed to improve the shifting quality further.



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*Source: 618587-2014-12-21.xml*