JPH0713483B2 - Automatic transmission control device for gas turbine vehicle - Google Patents

Description

The present invention relates to an automatic transmission control device for a gas turbine vehicle.

[Conventional technology]

In a two-shaft gas turbine engine, a compressor and a compressor turbine are connected by one compressor shaft, and an output turbine is attached to another output shaft. The gas generated by the combustion sequentially passes through the compressor turbine and the output turbine to drive the compressor and the output shaft, respectively. A variable vane nozzle is attached to the output turbine, and controlling the area of the variable vane nozzle enables efficient engine operation.

Generally, a reciprocating internal combustion engine is output controlled by the intake air amount according to the throttle valve opening and the fuel injection amount according to the adjust lever opening, and the output torque is controlled by the intake air amount and the fuel injection. It corresponds to the quantity. Therefore, when the output torque is used for controlling other devices, that is, the automatic transmission, the throttle opening and the accelerator opening can be directly used as parameters representing the output torque of the engine. However, the output torque of the two-shaft gas turbine engine corresponds to the accelerator opening,
Alternatively, they cannot be said to be proportional, and there is a considerable difference between the accelerator opening and the actual engine power. This is because the operation of the two-shaft gas turbine engine is performed in consideration of the surging region of the compressor, etc. Therefore, the fuel supply amount that is considered to govern the engine output torque is not directly proportional to the accelerator opening. is there. Further, in the two-shaft gas turbine engine, the variable vane nozzle is also throttled as the partial load is increased, and the output torque becomes higher as the rotational speed becomes lower. Therefore, if the accelerator opening is used to control the automatic transmission of a vehicle equipped with a two-shaft gas turbine engine, an appropriate shift point cannot be obtained. Therefore, in order to control the automatic transmission of the automobile equipped with the two-shaft gas turbine engine, it is necessary to obtain the output torque according to the operating state of the engine. Japanese Patent Application No. 60-2189, which is the applicant's earlier application, discloses that the target position of the throttle lever is calculated based on the outlet pressure of the compressor of the gas turbine engine and the blade angle of the variable blade nozzle.

[Problems to be solved by the invention]

As disclosed in the above-mentioned prior application, the output torque of the engine can be calculated from the outlet pressure of the compressor and the blade angle of the variable blade nozzle, and the output torque obtained from this can be calculated more than that obtained from the accelerator opening. It can be said that the accuracy is good. However, even if the output torque of the engine is calculated from the outlet pressure of the compressor and the blade angle of the variable blade nozzle,
In terms of accuracy, it was still unsatisfactory for use in controlling automatic transmissions.

[Means for solving problems]

In order to solve the above problems, an automatic transmission control device for a gas turbine vehicle according to the present invention is a gas turbine vehicle having a two-shaft gas turbine engine and an automatic transmission, wherein the compressor for the two-shaft gas turbine engine is used. Output torque calculation means for calculating the engine output torque according to at least three different signals including a signal indicating the operating state of the output turbine, a signal indicating the operating state of the output turbine, and a signal indicating the rotational speed of the output turbine, Shift position control means for controlling the shift position of the automatic transmission based on the output torque calculated by the output torque calculation means.

[Work]

In the above configuration, the engine is operated according to the signal indicating the operating state of the compressor of the two-shaft gas turbine engine, the signal indicating the operating state of the output turbine (excluding the rotation speed), and the signal indicating the rotation speed of the output turbine. Calculate the output torque. Using the signal representing the operating state of the compressor and the signal representing the operating state of the output turbine, the steady state engine output torque of the engine can be calculated. However, since the engine output torque in the engine transient state cannot be calculated satisfactorily by using both of these signals alone, using a signal representing the rotational speed of the output turbine in addition to these signals will indicate the engine transient state. The included engine output torque can be better calculated.

At least one of the outlet pressure of the compressor and the rotational speed of the compressor can be used as a signal indicating the operating state of the compressor. There is a correspondence between the outlet pressure of the compressor and the rotation speed, and both represent the operating state of the compressor. Other factors can be used as signals that indicate the operating condition of the compressor. Further, at least one of the opening area of the variable blade nozzle and the outlet temperature of the output turbine, or another factor other than the rotational speed can be used as the signal indicating the output turbine operating state.

〔Example〕

FIG. 1 is a diagram showing a drive system of a gas turbine vehicle having a gas turbine engine 10 and an automatic transmission 12.

The gas turbine engine 10 includes a compressor 14, a compressor turbine 18 connected to the compressor 14 by a compressor 16, and an output turbine 20.
And the output turbine shaft 22 attached to the combustor
26 and a heat exchanger 28. Fuel is supplied to the combustor 26 via a metering valve 30. Further, a variable blade nozzle 32 is attached to the output turbine 20, and its blade angle can be controlled by an actuator 34. The actuator 34 and the metering valve 30 are controlled by a first controller (ECUI) 36. The detection signals of the accelerator pedal 38, the engine and other detectors are input to the first control device 36.

As is known, the gas turbine engine 10 sends the air compressed by the compressor 14 through a heat exchanger 28 to a combustor 26, where the hot combustion gases produced therein drive the compressor turbine 18 and the output turbine 20. It is driven. Power turbine 20
The combustion gas passing therethrough is exhausted through the heat exchanger 28. The metering valve 30 controls the amount of fuel. The variable blade nozzle 32 is an output turbine by controlling the blade angle.
By controlling the flow of fuel gas consumed at 20, for example, by narrowing the opening area when the load is low, the operating line is shifted to the surge side, and a high operating temperature is maintained to obtain highly efficient operation. The metering valve 30 and the variable vane nozzle 32 are controlled by each other, and since they influence the engine output torque independently of each other, as described above, the generated engine output torque is simply changed to the accelerator pedal 38. It cannot be evaluated by the stepping amount.

The output turbine shaft 22 is an automatic transmission via a reduction gear device 40.
Twelve input shafts (not shown) are connected, and the output shaft of the automatic transmission 12 is transmitted to the wheels 44 via the differential gear unit 42. The automatic transmission 12 has a torque converter 46, a lockup clutch 48, and a planetary gear device 50, and the shift position can be controlled by hydraulically controlling the lockup clutch 48 and the planetary gear device 50 as is known. It is possible. The hydraulic pressure for controlling the shift position is achieved by a plurality of solenoid valves 52, which are connected to a second control device (EC
It is controlled by U2) 54. The second control device 54 receives at least three signals representing the operating state of the gas turbine engine 10, calculates the output torque accordingly, and based on the output torque thus calculated, the automatic transmission 12 operates. It controls the shift position.

FIG. 3 shows a shift example of the automatic transmission 12 determined according to the vehicle speed and the output torque. The solid line shows the upshift and the chain line shows the downshift. Vehicle speed is automatic transmission 12
The output torque can be directly detected from the rotational speed of the output shaft, and the output torque is calculated by receiving at least three signals representing the operating state of the gas turbine engine 10 as described above. In the case of the conventional reciprocating internal combustion engine, the output torque is represented by the throttle opening, and the throttle valve is divided between fully open and fully closed. Also in the present invention, the output torque can be accurately calculated between the maximum output torque and the minimum output torque with the same number of divisions as in the conventional case, as in the conventional case.

For this output torque calculation, as shown in FIG. 2, for example, the outlet pressure P ₃ of the compressor 14, the rotational speed N ₁ of the compressor 14, the rotational speed N ₃ of the power turbine 20, power turbine Sensors are provided for detecting the outlet temperature T _{6 of} 20, the opening area A of the variable vane nozzle 32, and the air temperature K, for example, which represents atmospheric conditions. These sensors are indicated in FIG. 2 by the reference numerals 56 to 66, respectively. In the present invention, the opening area A of the variable vane nozzle 32 is utilized by utilizing that the opening area A of the variable vane nozzle 32 corresponds to the position X _VN of the oil-filled actuator 34 as shown in FIG. The position is detected by detecting X _VN . Thereby, the opening area A of the variable vane nozzle 32 can be easily and accurately known. The control unit 54 is configured as a microcomputer, and has a central processing unit (CPU) 56 having arithmetic and control functions, a read only memory (ROM) 58 storing a program, and a random access memory (RAM) storing data and the like. ) 60, which are connected to each other by a bus 62 and also to an input / output interface 64. The detection signal of the above-mentioned sensor is inputted through the input / output interface 64, and the control signal is sent from the input / output interface 64 to the solenoid valve 52 for controlling the shift position of the automatic transmission 12.

FIG. 5 shows a flow chart for controlling the automatic transmission 12, and in step 70, a signal representing the operating state of the gas turbine engine 10 detected by various sensors,
That is, the outlet pressure P _{3 of} the compressor 14, the rotational speed N ₁ of the compressor 14, the rotational speed N _{3 of} the output turbine 20, the outlet temperature of the output turbine 20.
Read T ₆ , the opening area A of the variable vane nozzle 32, and the temperature K and pressure P ₀ of the air that represent atmospheric conditions. Next Step 71
Engine output torque TQ according to the signal detected at
Calculate ₃ . The engine output torque TQ ₃ is calculated in the form of f (P ₃ , N ₁ , N ₃ , T ₆ , A) which is a function of each detected amount. Next, in step 72, the vehicle speed V is read, and in step 73 it is determined whether or not a shift change condition is satisfied. The shift change conditions are stored as a two-dimensional map of the vehicle speed V and the engine output torque TQ ₃ as shown in FIG. If yes, go through step 74 to make a shift change, and if no, end the process as is.

In calculating the engine output torque TQ ₃ , in the embodiment, five detection signals, that is, the output power of the compressor 14 is output.
P ₃ , the speed N ₁ of the compressor 14, the speed N ₃ of the output turbine 20,
The outlet temperature T ₆ of the output turbine 20 and the opening area A of the variable vane nozzle 32 are used. And the engine output torque TQ ₃
Is calculated in the form of f (P ₃ , N ₁ , N ₃ , T ₆ , A), which is a function of each detected amount. That is, the relational expression of TQ ₃ = f (P ₃ , N ₁ , N ₃ , T ₆ , A) is prepared. When shown embodying _{this, TQ 3 = (aP 3 +} b) f (T 6, N 3) - (cA + d) f (N 1) is obtained. This equation can also be expressed as:

_{TQ 3 = (aT 6 P 3} + bN 3) - (cN 1 A + d) Thus, in the present invention the engine output torque TQ ₃
Is characterized in that it is calculated in the form of a function of each detection signal representing the engine operating state. This function is based on the two signals used in the above-mentioned prior application, namely, the outlet pressure P ₃ of the compressor 14 and the opening area A of the variable vane nozzle 32. 20 outlet temperature T ₆ , output turbine 20 speed N ₃ , compressor 14 speed
N ₁ is used in the form of a correction coefficient as a variable. In the examples, five variables to compute the engine output torque TQ _3, P _3, N _1, N _3, but using T _6, A, the engine output torque when using a minimum of three variables TQ
The calculation accuracy of ₃ can be improved more than before.

For example, among the five variables, the engine speed N ₁ of the compressor 14 there is a corresponding relationship between the outlet pressure P ₃ of the compressor 14 as shown in Figure 6, relates to the rotational speed N ₁ of the compressor 14 Information is obtained from the outlet pressure P ₃ of the compressor 14. In addition, the output turbine 20
The rotation speed N ₃ can be estimated from the opening area A of the variable vane nozzle 32 and the rotation speed N ₁ of the compressor 14. However, the rotational speed N ₃ of the output turbine has such a relationship in the steady state of the engine, but loses such a relationship in the transient state of the engine. Therefore, it is necessary to use the rotational speed N ₃ of the output turbine as a signal representative of the transient state of the engine. The information that cannot be obtained from the outlet pressure P ₃ of the compressor 14 and the opening area A of the variable vane nozzle 32 is a signal representing the combustion state, and the outlet temperature T ₆ of the output turbine 20 represents this information. Therefore, if the outlet pressure P ₃ of the compressor 14, the opening area A of the variable vane nozzle 32 and the outlet temperature T ₆ of the output turbine 20 are used, the engine output torque TQ ₃ can be calculated accurately. Then, by using the rotation speed N ₃ of the output turbine, the engine output torque TQ ₃ including the transient state of the engine can be accurately calculated. Especially for controlling the shift position of the automatic transmission,
It is important to know the engine output torque during engine transients. In this case, at least three different signals including a signal indicating the operating state of the compressor 14, a signal indicating the operating state of the output turbine 20, and a signal indicating the rotational speed of the output turbine 20 may be used. . Compressor
As the signal indicating the operating state of 14, at least one of the outlet pressure P ₃ of the compressor 14 and the rotation speed N ₁ of the compressor 14 or the equivalent may be used. Further, since the opening area A of the variable blade nozzle 32 basically controls the operation of the output turbine 20, the opening area A of the variable blade nozzle 32 and the output turbine 20 are signals representing the operating state of the output turbine 20. At least one of the 20 outlet temperatures T ₆ or equivalent may be used. And further, the rotation speed N _{1 of the} compressor 14
In addition, the accuracy can be further improved by using a signal indicating the atmospheric condition.

〔The invention's effect〕

As described above, according to the present invention, the engine output torque can be accurately calculated, and the shift position of the automatic transmission can be controlled using the accurately calculated engine output torque. It is possible to maximize the dynamic performance.

[Brief description of drawings]

FIG. 1 is a block diagram of a gas turbine vehicle according to the present invention, FIG. 2 is a detailed view of the control device of FIG. 1, FIG. 3 is a view showing a shift position of an automatic transmission, and FIG. FIG. 5 is a diagram showing the relationship between the opening area and the position of its actuator, FIG. 5 is a flowchart of the control of the automatic transmission, and FIG. 6 is a diagram showing the relationship between the outlet pressure of the compressor and the rotational speed. 10 …… engine, 12 …… automatic transmission, 14 …… compressor, 18 …… compressor turbine, 20 …… output turbine, 26 …… combustor, 32 …… variable blade nozzle, 54 …… controller.

Claims (1)

[Claims] 1. A gas turbine vehicle having a two-shaft gas turbine engine and an automatic transmission, and a signal representing an operating state of a compressor of the two-shaft gas turbine engine,
Output torque calculation means for calculating the engine output torque in response to at least three different signals including a signal representing the operating state of the output turbine and a signal representing the rotational speed of the output turbine; And a shift position control means for controlling the shift position of the automatic transmission on the basis of the output torque.