JPH0585791B2 - - Google Patents

Description

[Detailed description of the invention]

(Industrial Application Field) The present invention relates to a shift actuator control device, and particularly to a shift actuator control device that smoothly performs gear disengagement. (Prior art) As shown in Fig. 1, a shift actuator 1
consists of a cylinder part 1a and a piston part 1b, and the piston part 1b has a piston rod 1b ₁ with a diameter φA, an enlarged part 1b ₂ with a diameter φB, and a diameter φC.
It has a protruding rod 1b ₃ having an outer diameter φD and a ring portion 1b ₄ having an inner diameter φC. Therefore, each thrust becomes: F ₁ : Force acting on enlarged part 1b ₂ when solenoid valve V ₁ is open (i.e., R (gear input/output to reverse side) = P (π
φB ² /4−πφA ² /4) F ₂ : Force acting on the protruding rod portion 1b ₃ when the solenoid valve V ₂ (i.e., gear input/output to the L (low) side) = P (π
φC ² /4) F ₃ : Force acting on ring portion _1b4 when solenoid valve V ₂ is open (i.e. gear pulling force acting on ring portion) = P(π
φD ² /4−πφC ² /4) F ₄ : Force acting on the enlarged portion 1b ₂ and protruding rod portion 1b ₃ when the solenoid valves V ₁ and V ₂ are open (i.e., gear removal force acting on the piston rod) = F ₁ − It becomes F ₂ . Here, P is oil pressure. Further, it is designed such that F ₄ <F ₂ <F ₁ <F ₃ , and approximately F ₃ /F ₄ ≧2 holds true. Under these conditions, it is necessary to satisfy the following conditions. (1) F ₁ must not exceed the allowable shift force (limit value) of the shift actuator, (2) F ₂ must work within the allowable shift time of the shift actuator (does not cause any discomfort to the driver). (3) F ₄ = F ₁ - _{F 2} must be the thrust that allows the gear to be pulled out; (4) The piston rod of the shift actuator must not lose speed when shifting. , is required. (Problem to be solved by the invention) However, due to the following reasons, the above-mentioned force F ₄ ,
The selection of F ₂ is very difficult. (1) If the gear input (F ₂ ) to the L side is sufficiently large, the pulling force (F ₄ =F ₁ −F ₂ ) will be insufficient, leading to gear pulling failure and making it impossible to shift. In addition, if the above-mentioned problem occurs when parking in gear, automatic transmissions equipped with a safety mechanism that prohibits starting the engine in a position other than neutral will not be able to start the engine, resulting in vehicle damage. There is a risk that this may lead to (2) On the other hand, if you apply sufficient gear removal force (F ₄ ),
In other words, if F ₂ is chosen to be small, the gear input/output (F ₂ ) will be insufficient. As a result, the synchronization time becomes longer, that is, the shift time becomes longer, giving a bad feeling to the driver. (3) Furthermore, even if appropriate gear input and gear removal forces are set, if the oil pressure falls below the specified value, the gear will not be able to be removed. As a result, it becomes impossible to start the engine. Further, even if the engine starts, for example, there is a possibility that a state in which the gear cannot be changed may occur. (4) Additionally, the viscosity of the lubricating oil in the cold-time transmission increases, increasing the sliding resistance, and the gear pulling force is required to be much larger than under normal conditions (approximately twice as much). As a result, the gear cannot be pulled out properly, making it impossible to start the engine. Furthermore, even if the engine starts, there is a possibility that a state in which the gears cannot be changed may occur. In order to solve this problem, it is possible to consider changing the cylinder size of the shift actuator 1, but this is impossible because it would take a lot of time and effort to change the design, and the cost of changing the design would be enormous. . Therefore, an object of the present invention is to use a shift actuator with the same cylinder size as the conventional one, so that when the transmission is shifted out of gear in the direction where the operating force is the weakest, the shift actuator can shift smoothly into neutral. An object of the present invention is to provide a shift actuator control device capable of gear removal. (Means for Solving the Problems) In order to achieve the above-mentioned object, according to the present invention, a plurality of pistons of different diameters are arranged in a cylinder, and three A control device for a shift actuator that selectively stops a piston at a specific piston stop position includes a temperature sensor that measures the temperature of lubricating oil inside the transmission, and a temperature sensor that is connected to the transmission to stop the piston at the neutral position and on both sides thereof. The piston rod has a first and second operating position, and the piston rod takes the first operating position by applying hydraulic pressure by opening the first solenoid valve, and takes the above-mentioned first operating position by applying hydraulic pressure by opening the second solenoid valve. It assumes the second operating position, and takes the neutral position by applying hydraulic pressure by opening the first and second solenoid valves, and the actuation force of the piston rod to the second operating position is greater than the operating force of the piston rod to the first operating position. When a neutral position movement command is issued from the second operating position of the piston rod with the shift actuator having low power and the temperature detected by the temperature sensor being lower than a predetermined value, the first and second solenoid valves are opened. A shift actuator control device is provided, comprising: electromagnetic valve driving means for opening only a second electromagnetic valve prior to operation. (Function) When a stopped vehicle with the engine stopped is about to start and the gear is shifted from the L side to the neutral direction, the shift stroke sensor detects where the shift stroke position is, and the gear position is detected by the shift stroke sensor. When the shift actuator is on the L side and the actuation force to remove the gear from the L side in the neutral direction is weaker than the actuation force of the shift actuator to remove the gear from the opposite direction, only one solenoid valve is actuated to move the piston rod at once. After bringing the gear to the R side, the two solenoid valves are operated to bring it to the neutral position, and the gear is removed to maintain the neutral position. (Example) Next, an example of the present invention will be described with reference to the drawings. FIG. 1 is an enlarged block diagram of a shift actuator used in the present invention, FIG. 2 is a schematic block diagram of an embodiment of a transmission actuator using the shift actuator of the present invention, and FIG. The diagram is
This is a flowchart of gear release control. In addition, in the following explanation, FIG.
As shown in the figure, the shift actuator of the present invention has a gear pulling force (F ₄ ) from the L side to the neutral.
is the gear pulling force from the R side to neutral (F ₃ )
The explanation will be based on the assumption that it is arranged so that it is smaller, but it is also possible to arrange it so that it is the opposite of this case, so in that case,
“L” and “R” should be read interchangeably. The shift actuator shown in FIG. 1 has already been described in connection with the prior art and will only be described briefly. In the shift actuator 1, when only the solenoid valve _V1 is turned on and opened, the hydraulic pressure acts on the right side of the enlarged portion _1b2 , pushing the piston rod _1b1 to the left side with the force of _F1 and moving it. (reverse) take up position. Furthermore, when only the solenoid valve _V2 is turned on, hydraulic pressure acts on the left side of the protruding rod portion _1b3 of the piston rod _1b1 , moving the piston rod _1b1 to the right side.
Press and move with _F2 force to take the L (low) position. Also, if solenoid valves V ₁ and V ₂ are turned on at the same time,
The force F ₁ −F ₂ acts on the piston rod 1b ₁ , and the force F ₃ acts on the ring portion to take the neutral position. In this way, the shift actuator 1 has three positions. Next, an embodiment of a transmission actuator using the shift actuator of the present invention will be described with reference to FIG. 2 and Table 1. However, while the embodiment of FIG. 2 includes emergency controls, the invention is not limited to sometimes including emergency controls. In FIG. 2, TM is a well-known parallel shaft gear type transmission, 1 indicates a shift actuator of the transmission TM, and the first
It has the same structure and performs the same operation as shown in the figure. 2 indicates a select actuator. The select actuator 2 is a cylinder 2
A piston P21 provided on a piston rod 2b connected to the selection rod of the transmission TM and a piston P22 loosely fitted to the end of the piston rod 2b are built into the cylinder a, and the left end of the cylinder 2a is equipped with other pistons. A piston P23 is provided, and the cylinder 2a has hydraulic chambers 2c, 2.
d, 2e are formed. When applying hydraulic pressure to the three hydraulic chambers of the select actuator 2 as described later, the piston rod 2b can take four positions. At this time,
The transmission TM is neutral N ₁ , N ₂ ,
It will be placed at either position N ₃ or N ₄ . 3 indicates a shift stroke sensor consisting of a variable resistor, for example, and the shift actuator 1
The position of the piston rod _1b1 is detected over the entire stroke, and a position signal TMS of the piston rod _1b1 that changes every moment is output. S ₁ to _{S 4} are switches for detecting each of the aforementioned select positions of the select actuator neutral, and one of the switches S ₁ to _{S 4} is turned on according to each select position. , select position signal
It outputs TMC. V ₁ , V ₂ are solenoid valves that operate the shift actuator 1, and V ₃ ,
V ₄ and V ₅ are solenoid valves that operate the selection actuator 2. Pin is the main oil pressure source, P is the oil pressure source for the normal hydraulic circuit system, and P' is
Serves as a hydraulic power source for the emergency hydraulic circuit system. In addition,
In the present invention, not only hydraulic pressure but also pneumatic pressure is included. Ve ₁ is an emergency solenoid valve for the selector actuator 1, Ve ₂ and Ve ₃ are emergency solenoid valves for the shift actuator, and Ve ₄ is
This is a solenoid valve for switching the hydraulic circuit system. Reference numeral 4 denotes a dry single-plate clutch, which is connected to the output shaft of an engine (not shown) on the input side of the transmission TM, and the output shaft is connected to the input shaft of the transmission TM. A release fork 4a of the clutch 4 is connected to a clutch actuator 5. clutch actuator 5
has a piston 5b moving within the cylinder 5a, which piston 5b is connected to the clutch 44 as described above.
The piston 2b is further connected to a clutch stroke sensor 6, which is a variable resistor, for example. The clutch actuator 5 is connected to electromagnetic valves V ₆ , V ₇ , and V ₈ for operating the clutch actuator 5 . The solenoid valve _V8 has a smaller port diameter than the solenoid valve _V7 . When solenoid valve V ₆ is opened with solenoid valves V ₇ and V ₈ closed, hydraulic pressure is applied to hydraulic chamber 5c of clutch actuator 5, and piston 5b moves to the right in FIG. is prohibited. When the solenoid valve V ₈ with a small port diameter or _the solenoid valve V ₇ is opened simultaneously or separately with the solenoid valve V 6 closed, the oil pressure in the hydraulic chamber 5c decreases and the oil filled therein decreases. is pulled out in the direction of the tank T, so the piston 5b moves to the left by the spring force of the clutch 4, and the clutch 4 changes from the disengaged state to the engaged state. The operating speed of the clutch 4 from disengagement to engagement can be adjusted by adjusting the degree of oil drainage by adjusting the degree of opening of the solenoid valves V ₇ and V ₈ . The operating position of the clutch actuator 5, ie, the position of the clutch 4, is detected by a clutch stroke sensor 6, and the position signal is output as "CLUS".
7 is a temperature sensor that measures the temperature of the lubricating oil in the transmission TM, and outputs an oil temperature signal "TMT". 8 is a pressure gauge that measures the oil pressure of the oil pressure source that operates each actuator, and outputs an oil pressure signal "PRES". Reference numeral 9 denotes a control device configured as a macro computer. The control device 7 receives not only detection signals obtained from various parts of the vehicle but also commands issued by the driver or the like. In the present invention, in particular, the clutch stroke position signal "CLUS" emitted from the clutch stroke sensor 6, the engine rotation speed signal "ENGN" (detector not shown),
Position signal “TMS” indicating shift stroke from shift stroke sensor 3, select position signal “TMC” from switches S ₁ to _{S 4} , oil temperature sensor signal “TMT” from temperature sensor 7, oil pressure from pressure gauge Signal “PRES” is input. The control device 9 is configured to issue output signals to predetermined parts for controlling each part of the vehicle according to a program stored in advance in the memory MEM according to input commands and detection signals. The central processing unit CPU is used for execution. In the present invention, although not shown in the figure, the control device 9 uses the accelerator pedal depression amount signal and the engine speed "ENGN" to control the transmission.
The optimum gear change stage of the TM is calculated, a command signal is issued to each electromagnetic valve to operate them, and the shift actuator 1 and select actuator 2 are driven, as well as the clutch actuator 5 is driven. to switch the transmission TM to the optimal gear. In the present invention, as described above, the shift actuator 1 of the transmission TM is provided with the shift stroke sensor 3 to continuously detect the shift stroke and constantly monitor the gear position. If a gear is pulled out while a large torque is being generated in the transmission TM gear, the clutch 4 is temporarily disengaged and the gear is re-engaged. Additionally, if a gear slips out when the transmission TM gear is not generating a large amount of torque, the gear is automatically re-engaged without disengaging the clutch. Furthermore, if gear slippage occurs within a short period of time and the amount of gear slippage is greater than a predetermined value, the clutch 4 is temporarily disengaged and the gear is re-engaged. Next, normal solenoid valves (V ₁ , V ₂ , V ₃ , V ₄ , V ₅ )
Table 1 shows the relationship between the operating states of the emergency solenoid valves (Ve ₁ , Ve ₂ , Ve ₃ , Ve ₄ ) and the gear position.

[Table] As is clear from Table 1, emergency solenoid valves are used when normal solenoid valves fail. For example, the "R" gear position is determined by the solenoid valves Ve ₂ , Ve ₁ ,
Ve ₄ is obtained by turning on, and the “L” gear position is:
_The neutral position is obtained by turning on _{the solenoid valves Ve 3 ,} Ve ₁ and _{Ve 4 .} Next, the gear release control of the present invention will be explained with reference to the flowchart of FIG. First, it is assumed that the vehicle is stopped with the engine stopped, and the gear change position of the transmission is in the 1st (low) position, which is the state immediately before the vehicle stops. When the driver turns on the key switch and applies voltage to the control device 9 in order to drive the vehicle, the oil temperature signal "TMT" from the temperature sensor 7 and the shift The shift stroke signal “TMS” from the stroke sensor 3, the oil pressure signal “PRES” from the pressure gauge 8, and the engine speed signal “ENGN” from the engine are read into the work memory provided in the control device 9 (step S1
~S4). Next, it is determined whether the engine speed "ENGN" read in step S4 is zero (step S5). And if it is zero, that is, if it is confirmed that the engine has not been started yet,
In step 3, it is determined whether the read oil pressure signal "PRES" has reached or is lower than the set value. That is, it is determined whether the hydraulic pressure has reached a pressure sufficient to operate all actuators (step S6). If the oil pressure has already reached the set value, proceed to step S7 and set the oil temperature read in step S1.
If TMT has reached the set value and it is determined that the oil viscosity is not very high and that there is no large load on each actuator, solenoid valves V ₁ and V ₂
Open the hydraulic chamber 1c of the shift actuator 1.
Apply hydraulic pressure to and 1d at the same time (step S11),
1st transmission TM in normal operation
(low) to neutral. In step S7, if the oil temperature TMT is lower than the set value and the viscosity is high, the process moves to step S8, which will be described later. In step S8, the shift stroke position "TMS" from the shift stroke sensor read in step S2 is determined, and if the gear position of the transmission TM is on the Reverse (R) side, even if the oil pressure is low, Also, even if the oil temperature is low, the shift actuator 1 can be shifted from the R position to the neutral position by the operating force described above. Therefore, by opening both solenoid valves _V1 and _V2 , the shift actuator Hydraulic pressure is applied to hydraulic chambers 1c and 1d of No. 1 at the same time (step S11), and the transmission TM is moved from Reverse (R) to neutral gear using normal operation. At step S8, the shift stroke position “TMS” from the shift stroke sensor 3 is 1st.
If it is on the (low) side, the process moves to step S9, where solenoid valve _V1 is opened and solenoid valve _V2 is kept closed. In this operation, hydraulic pressure is applied only to the hydraulic chamber 1c of the shift actuator 1, and the gear of the transmission TM is moved to the 1st gear with a large force.
(low) side toward neutral, and this operation is continued until the transmission TM quickly passes through neutral and reaches Reverse (R) (step S10). When the transmission TM reaches the Reverse (R) position, the process moves to step S11, and the solenoid valve V ₁ and
V ₂ is opened, and the transmission TM is disengaged from the Reverse (R) position and shifted to the neutral position by the operation described above, and this position is maintained. After this operation is completed and it is confirmed that the gear disengagement operation has been completed, the engine is started. Of the above-mentioned operations shown in FIG. 3, when the transmission TM is switched, the clutch 4 is placed in the disengaged state by a command from the control device 9, but since the explanation would be complicated, we will not explain the details of the clutch operation. Explanation has been omitted. (Effects of the Invention) As explained above, the present invention provides the following advantages: when removing a gear to the neutral position, or from a direction where the gear removing force is considered to be weak,
Since the gear is pulled out after passing through the neutral position and shifting to the opposite side, the gear can be pulled out smoothly even if the shift actuator has the same size piston as the conventional one.
Moreover, even when the oil pressure is low and/or the oil temperature is low, the gear can be smoothly disengaged.

[Brief explanation of the drawing]

FIG. 1 is an enlarged block diagram of a shift actuator used in the present invention, FIG. 2 is a schematic block diagram of an embodiment of a transmission actuator using the shift actuator of the present invention, and FIG. The figure is a flowchart of gear disengagement control. 1...Shift actuator, 1a...Cylinder, 1b...Piston rod, 2...Select actuator, 3...Shift stroke sensor,
7...Temperature sensor, 8...Pressure gauge, 9...Control device, _V1 , _V2 , _V3 , _V4 , _V5 ...Solenoid valve, TM...
Transmission.

Claims (1)

[Scope of Claims] 1. A shift actuator in which a plurality of pistons of different diameters are arranged in a cylinder, and the pistons are selectively stopped at three piston stop positions depending on the state of oil pressure applied to each piston. The control device includes a temperature sensor for measuring lubricating oil temperature inside the transmission, and a piston rod connected to the transmission and having a neutral position and first and second operating positions on both sides thereof, the piston rod having: The first working position is taken by applying hydraulic pressure by opening the first solenoid valve, the second working position is taken by applying hydraulic pressure by opening the second solenoid valve, and the second working position is taken by opening the first and second solenoid valves. A shift actuator that assumes a neutral position by applying hydraulic pressure and has a smaller actuation force for moving the piston rod to a second actuation position than the actuation force for moving the piston rod to the first actuation position; and a shift actuator whose temperature detected by the temperature sensor is a predetermined value. Solenoid valve driving means for opening only the second solenoid valve prior to opening the first and second solenoid valves when a neutral position movement command is issued from the second operating position of the piston rod in a state where the piston rod is lower than the first position. A shift actuator control device comprising: