JPH06264997A - Speed change control method and device of speed change - Google Patents

Abstract

PURPOSE:To control the rotational speed of a counter shaft so as to enable smooth speed change operation by calculating the target rotational speed of the counter shaft for allowing the speed change operation, and controlling connection/disconnection of two clutches. CONSTITUTION:A first clutch 5 for accelerating the rotation of a counter shaft 16 and a second clutch 6 for decelerating rotation of the counter shaft 16 by connecting/disconnecting the counter shaft 16 and an output shaft 8 are provided. The target rotational speed of the counter shaft 16 for allowing speed change operation is calculated from the number of gears to be subjected to speed change operation and the rotational speed of the prevent output shaft 8. And the first clutch 5 is operated when the prevent rotational speed is smaller than the target rotational speed and the rotation of the counter shaft 16 is increased and decreased when it is larger than it. The speed change operation is performed when the difference of this rotational speed is less than a specified value. Consequently, a comfortable operational performance can be secured.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a shift control method and device for a transmission, and more particularly to a target of a counter shaft which permits a shift operation based on the number of teeth of a gear selected by a shift operation and the rotational speed of an output shaft. The number of revolutions is calculated and the two clutches provided on the side of the transmission are connected / disconnected to control the number of revolutions of the counter shaft to approach the target number of revolutions before the gear change operation is performed, resulting in a smooth gear change operation. The present invention relates to a speed change control method and device for a speed change device, which can perform the operation in a short time.

[0002]

2. Description of the Related Art Conventionally, when shifting the gears of a vehicle transmission, the shift operation is performed after the clutch is operated to disconnect the transmission from the engine, but as an automatic transmission, An automatic transmission that automatically shifts the manual transmission to an actuator that uses a fluid pressure cylinder has been adopted. By not using a torque converter, fuel efficiency is improved and driving loss is dramatically reduced while reducing output loss. Improved transmissions have been put to practical use.

However, in this type of automatic transmission, a mechanical clutch is mainly used, and in this type, the clutch must be engaged and disengaged each time a gear shifting operation is performed. .

Therefore, when the clutch is disengaged prior to the gear shifting operation, the rotary members below the clutch disk rotate inertially due to their inertia, so that they are fixed to the input shaft, the input gear, the counter gear, the counter shaft, and the counter shaft. The main gear for speed change will rotate by inertia together.

When the clutch is not completely disengaged, so-called clutch dragging occurs, but even in this case, the counter shaft and the like continue to rotate at a certain speed against the driver's will.

On the other hand, in order to smoothly perform the gear insertion and gear removal of the transmission, it is necessary to perform a gear shift operation in a state where the rotation speeds of the output shaft and the main gear are synchronized.

That is, when the gear is upshifted, the rotational speed of the main gear connected next is always higher than the rotational speed of the output shaft, so it is necessary to reduce the rotational speed of the main gear prior to shifting, and vice versa. When the gear is downshifted, the rotation speed of the main gear to be connected next is always lower than the rotation speed of the output shaft. Therefore, it is necessary to increase the rotation speed of the main gear before shifting.

In order to reduce or increase the rotational speed of the main gear, conventionally, a double clutch operation is performed, or the conical inner diameter of the synchronizer ring is brought into contact with the conical portion of the main gear, and the frictional force of the conical portion causes frictional force of the main gear. After synchronizing the rotation speed and the rotation speed of the output shaft, the gear shift operation is performed using a so-called synchromesh mechanism that causes the gears to mesh with each other.

However, according to the conventional synchronization method and apparatus,
It takes a long time to synchronize the rotation speed of the main gear and the rotation speed of the output shaft, and the gear shift may occur at a timing that is slightly different from the driver's intention, so there is room for improvement in order to ensure light driving performance. there were.

[0010]

SUMMARY OF THE INVENTION The present invention has been made to eliminate the above-mentioned drawbacks of the prior art. The object of the present invention is to provide an output gear driven by a synchro gear fixed to an output shaft. A first clutch that connects or disconnects the gear and the synchro shaft, and a second clutch that connects or disconnects the synchro shaft and the case of the transmission, and activates the first clutch during gear downshifting. The rotation speed of the synchro shaft is increased, and when the gear is upshifted, the second clutch is operated to reduce the rotation speed of the synchro shaft, and the counter gear and the main gear that are spline-fitted to the synchro shaft are used for counter operation. By increasing or decreasing the speed of the shaft, the main gear and output shift can be And that to be able to synchronize the rotational speed of the shift and thereby is to ensure a nimble operation performance to be able to perform the gear shift operation to the will by a driver.

Another object of the present invention is to set a target rotational speed of the counter shaft which allows the gear shifting operation based on the number of gear teeth to be shifted and the current rotational speed of the output shaft, and the target rotational speed and the current rotational speed of the counter shaft. Is to calculate the permissible range of the difference in the number of revolutions between the and, and when the difference in the number of revolutions is within the permissible range, to allow the transmission to perform a gear shifting operation. It is to be able to perform a smooth shift operation.

Still another object is to set an allowable range of the rotational speed difference to an optimum value determined in advance from the rate of change of the rotational speed difference for each acceleration pattern or deceleration pattern of the counter shaft with respect to time and the temperature of the transmission oil. By using this control, it is possible to always perform a smooth gear shift operation regardless of whether the gear is upshifted or downshifted.

[0013]

In summary, the method of the present invention (claim 1) comprises a first clutch for connecting or disconnecting the counter shaft and the output shaft to accelerate the rotation of the counter shaft, and the counter shaft. A second clutch that connects or disconnects the case of the transmission to reduce the rotation of the counter shaft is used, and the shift operation is permitted based on the number of gear teeth to be gear-shifted and the current rotation speed of the output shaft. A target rotation speed of the counter shaft is calculated, and when the current rotation speed of the counter shaft is smaller than the target rotation speed, the first clutch is operated to accelerate the rotation of the counter shaft, and the current rotation speed is When the rotational speed is higher than the target rotational speed, the second clutch is activated to decelerate the rotation of the counter shaft. So, the difference between the current rotational speed of the counter shaft and the target rotational speed is characterized in that to perform the shifting operation of the transmission device when it becomes smaller than a predetermined value.

The device of the present invention (claim 3) includes a first clutch for connecting or disconnecting the counter shaft and the output shaft, and a second clutch for connecting or disconnecting the counter shaft and the case of the transmission. , Output shaft rotation speed detection device that detects the rotation speed of the output shaft, counter shaft rotation speed detection device that detects the rotation speed of the counter shaft, oil temperature sensor that detects the temperature of the transmission oil, A gear position sensor for detecting a transmission gear position, a target rotation speed of the counter shaft that allows the shift operation is calculated from the number of teeth of a gear selected by the shift operation, and the rotation speed of the output shaft, and the counter is operated. Current shaft speed is less than the target speed Control that sometimes activates the first clutch to accelerate the rotation of the counter shaft, and activates the second clutch to decelerate the rotation of the counter shaft when the current rotational speed is greater than the target rotational speed. And a device.

[0015]

DESCRIPTION OF THE PREFERRED EMBODIMENTS The present invention will be described below with reference to the embodiments shown in the drawings. 1 and 2, a shift control device 1 for a transmission according to the present invention includes a first clutch 5, a second clutch 6, an output shaft rotation speed detection device 50,
Counter shaft rotation speed detection device 51 and oil temperature sensor 5
2, a gear position sensor 53, and a computer 22 which is an example of a control device.

The shift control device 1 includes a first speed main gear 9A and a reverse main gear 9 which are rotatably fitted to the output shaft 8 and the output shaft 8.
B for synchronizing the rotation speed of the second-speed main gear 9C, the third-speed main gear 9D, or the fourth-speed main gear 9E, and a constant mesh gear type transmission device 10.
Is attached to.

First, the structure of a constant mesh gear type transmission 10 with a synchronizing device will be described. A clutch 14 such as a hydraulic pressure type is arranged between a crankshaft 12 and an input shaft 13 of an engine (not shown). The crankshaft 12 and the input shaft 13 are connected and disconnected.

The input gear 15 fixed to the input shaft 13 meshes with the counter gear 18 fixed to the counter shaft 16, and transmits the rotation of the input shaft 13 to the counter shaft 16.

A counter gear 16A for the first speed, a counter gear 19B for the second speed, a counter gear 19C for the second speed, a counter gear 19C for the third speed, a counter gear 19D for the fourth speed and a counter gear 19E for the fourth speed are fixed to counter shaft 16, respectively. Main gear 9A, reverse main gear 9B, second speed main gear 9C,
It meshes with the third-speed main gear 9D and the fourth-speed main gear 9E.

Between the first speed main gear 9A and the reverse main gear 9B of the output shaft 8, between the second speed main gear 9C and the third speed main gear 9D, and between the fourth speed main gear 9E and the input gear 15. , Gear shift shift forks 20A, 20B and 20C are provided respectively, and the shift select unit 23 is operated by an instruction from the computer 22 by manually operating the shift lever 21 to shift the shift forks 20A, 20B or 2
0C to move each sleeve 17A, 17B or 17
1st speed main gear 9A through C, reverse main gear 9
B, a second-speed main gear 9C, a third-speed main gear 9D, and a fourth-speed main gear 9E are configured to be connected to any of the main gears and the output shaft 8.

The synchro gear 2 is for transmitting the rotation of the output shaft 8 to the output gear 4, and is fixed to the output shaft 8 so as to rotate together with the output shaft 8.

The synchro shaft 3 controls the rotation speed of the synchro shaft 3 so that it is connected to the first speed main gear 9A, the reverse main gear 9B,
The main gear 9C for the second speed, the main gear 9D for the third speed, or the main gear 9E for the fourth speed are accelerated and decelerated to synchronize with the rotation speed of the output shaft 8, and the case of the constant mesh gear type transmission 10. 27 is rotatably supported by a ball bearing (not shown).

A male spline is formed at an intermediate portion of the synchro shaft 3, and a female spline formed on the counter gear 25 is slidably fitted to the male spline.

The counter gear 25 is the second speed main gear 9
It is meshed with C and is configured to transmit the rotation of the synchro shaft 3 to the counter shaft 16 via the second speed main gear 9C and the second speed counter gear 19C.

The output gear 4 is for transmitting the rotation of the output shaft 8 to a first clutch 5 which will be described later, and is rotatably fitted to the synchro shaft 3 and meshed with the synchro gear 2. The output shaft 8 is driven to rotate.

A ring-shaped protrusion 4a is provided on the side of the output gear 4 and is configured as a housing for the first clutch 5.

The first clutch 5 is a first speed main gear 9
A, reverse main gear 9B, second speed main gear 9C, 3
It is for increasing the rotation speed of the main gear for speed 9D or the main gear for fourth speed 9E, and an intermediate ring (not shown) is slidably fitted to the synchro shaft 3 so as to transmit the rotational force. is doing.

A plurality of shaft side clutch plates 29 are slidably spline-fitted to the outer peripheral portion of the intermediate ring.

A female spline is formed on the inner diameter of the ring-shaped protrusion 4a formed as the housing of the first clutch 5, and is slidable with a male spline (not shown) formed on the housing side clutch plate 30. A plurality of housing side clutch plates 30 and a plurality of shaft side clutch plates 29 are alternately arranged and housed in the housing.

A cylinder chamber (not shown) is provided opposite to the side of the shaft side clutch plate 29 and the housing side clutch plate 30, and a first piston (not shown) is provided in the cylinder chamber left and right in FIG. It is fitted so that it can slide in any direction.

An O-ring (not shown) is attached to the inner and outer diameter fitting portions of the first piston and the cylinder chamber to maintain airtightness, and a compression spring (not shown) allows the first piston to engage the first side clutch with the shaft side clutch. The plate 29 and the housing-side clutch plate 30 are urged in the direction of disengagement (rightward in FIG. 2).

Then, the compressed fluid is supplied from the compressed fluid supply source 56 to the compressed fluid supply port (not shown) provided in the case 27 through the fluid switching valve 58A to move the first piston to the position shown in FIG.
When the shaft side clutch plate 29 and the housing side clutch plate 30 are brought into close contact with each other by moving in the left direction, the rotational force of the output gear 4 is transmitted to the synchro shaft 3 by a frictional force.

The second clutch 6 is a first speed main gear 9
A, reverse main gear 9B, second speed main gear 9C, 3
The first clutch 5 is for reducing the rotational speed of the high speed main gear 9D or the fourth speed main gear 9E.
And the structure is almost the same.

Fixed housing 4 fixed to case 27
A fixed clutch plate 41 is slidably fitted into the inside of 0, and a female spline (not shown) of the shaft side clutch plate 42 is attached to a male spline (not shown) formed continuously with the counter gear 25. ) Slidably fixed clutch plate 41
And a plurality of sheets are alternately arranged and fitted.

A cylinder portion (not shown) is formed in the fixed housing 40 in the same manner as the cylinder chamber of the first clutch 5, and a second piston (not shown) has an O-ring (shown in the figure) in the cylinder portion. It is fitted slidably in the left-right direction via (not shown).

A compression spring (not shown) is attached to the second piston, and is attached in a direction (leftward in FIG. 2) for separating the second piston from the fixed clutch plate 41 and the shaft side clutch plate 42. I am energetic.

Then, the compressed fluid is supplied from the compressed fluid supply source 56 to the compressed fluid supply port (not shown) provided in the case 27 through the fluid switching valve 58B to move the second piston to the position shown in FIG.
By moving the fixed clutch plate 41 and the shaft side clutch plate 42 in close contact with each other, the braking force is transmitted to the synchro shaft 3 by a frictional force.

A lubricating oil supply hole is formed in each of the synchro shaft 3, the output gear 4, the counter gear 25 and the intermediate ring, and a lubricating oil supply device (not shown) is provided.
Lubricating oil is supplied to lubricate each part.

Output shaft speed detector 50
Is for detecting the number of rotations of the output shaft 8 and is a constant mesh gear type transmission 1.
This is a rotation speed detection device using, for example, a Hall element, which is arranged in the vicinity of the output shaft 8 of 0, and generates an electric pulse proportional to the rotation speed of the output shaft 8.

The counter shaft rotation speed detecting device 51 is
A rotation speed detection device for detecting the rotation speed of the counter shaft 16 is provided in the vicinity of the counter shaft 16 and uses, for example, a Hall element. Pulse is generated.

The oil temperature sensor 52 is for detecting the oil temperature of the transmission oil, and is, for example, a thermistor whose electric resistance value changes in proportion to the temperature, so that the detecting portion contacts the transmission oil. It is disposed in the constant mesh gear type transmission 10.

The gear position sensor 53 is for detecting the position of the currently selected gear, and is a micro switch, for example, and is attached to the shift select unit 23. A lever position sensor 54 is provided on the shift lever 21, and detects the position of the shift lever 21 selected to shift gears.

The above-mentioned sensors are connected to the signal lines 55A, 5
5B, 55C, 55D and 55E are electrically connected to the computer 22.

The computer 22 as an example of the control device is
Various information is input from the output shaft rotation speed detection device 50, the counter shaft rotation speed detection device 51, the oil temperature sensor 52, the gear position sensor 53, the lever position sensor 54, and the like, and based on the information, the first clutch 5, This is a well-known computer device for optimally controlling the second clutch 6, the shift select unit 23, and the like, and including a central processing unit 22a, an input / output port 22b, an external storage device 22c, and the like.

The present invention is configured as described above,
The operation will be described below. 1 to 3, when the vehicle is traveling at the first speed, for example, the sleeve 17A is engaged with the first speed main gear 9A by the shift fork 20A for gear shifting, and the rotational force of the crankshaft 12 of the engine 11 is increased. Is transmitted to the input shaft 13 by the clutch 14.

Further, the input gear 15 and the counter gear 1
8, counter shaft 16, first speed counter gear 19
Rotational force is transmitted to the output shaft 8 through the A first-gear main gear 9A and the sleeve 17A.

That is, the rotational torque input from the engine 11 in the direction of arrow F is output from the output shaft 8 in the direction of arrow G to rotate the wheels (not shown) to drive the vehicle.

When a clutch pedal (not shown) is operated to change the speed, the clutch 14 disconnects the crankshaft 12 from the input shaft 13, and the speed change lever 21 is manually operated.
Is the gear position sensor 53 in step S ₁ of FIG.
The position of the currently selected gear is read from, and the gear position to be changed is read from the lever position sensor 54 and input to the computer 22. And the computer 22
Operates the shift select unit 23 to remove gears.

Specifically, for example, in the case of shifting from the 1st speed to the 2nd speed, the shift fork 20A for shifting the gear moves leftward in FIG. 2 on the output shaft 8 and the sleeve 17A moves in the same direction. By doing so, the engagement between the first-speed main gear 9A and the output shaft 8 is released.

In this state, the input shaft 13, the input gear 15, the counter gear 18, the counter shaft 16 and the counter gear 19A for the first speed, the counter gear 19B for the reverse drive, the counter gear 19C for the second speed, and the counter gear 19C for the second speed, Third-speed counter gear 19D, fourth-speed counter gear 19E, first-speed main gear 9A, reverse main gear 9B, and second-speed main gear 9 that mesh with these gears, respectively.
C, the third gear main gear 9D and the fourth gear main gear 9E are inertially rotating.

In step S ₂ , the output shaft rotation speed detection device 50 detects the rotation speed NU of the output shaft 8, and in step S ₃ , the counter shaft rotation speed detection device 51 detects the counter shaft 16.
The number of revolutions ND is detected. Further, in step S ₄ , the oil temperature T of the transmission oil is detected by the oil temperature sensor 52 and input to the computer 22.

The computer 22 calculates the target rotational speed NDT of the counter shaft 16 which permits the speed change from the number of gear teeth to be changed and the rotational speed NU of the output shaft 8 in step S ₅ .

In step S ₆ , it is judged whether or not the absolute value of the difference between the target rotation speed NDT and the current rotation speed ND of the counter shaft 16 is smaller than a predetermined value A which is determined in advance. If also small, the rotational speed of the rotational speed and the second speed main gear 9C of the output shaft 8 is in a state of substantially synchronized, the flow proceeds to step S ₇ through the route R _1, the first clutch 5 and After releasing the second clutch 6, a gear shift enable signal is transmitted in step S ₈ .

That is, according to a command from the computer 22, the shift fork 20B for gear shifting moves to the right in FIG. 2 and the sleeve 17B moves to the second speed main gear 9C.
By engaging with, the second speed main gear 9C and the output shaft 8 are connected, and the shift operation to the second speed is completed.

If the absolute value of the difference between the target rotation speed NDT and the current rotation speed ND is larger than the predetermined value A, it is determined in step S ₉ whether the target rotation speed NDT is larger than the current rotation speed ND. There is judged, it is judged that the greater a shift-down process proceeds to step S _10, to calculate the rate of change with respect to time of the difference in rotational speed.

Then, in step S ₁₁ , the threshold value of the acceleration pattern in the current state is obtained from the graph (FIG. 4) of the threshold value obtained experimentally as a function of the change rate of the difference in rotational speed with respect to time and the oil temperature T of the transmission oil. Find C.

[0057] Whether the difference between the current rotational speed ND of the target speed NDT and countershaft 16 at step S ₁₂ is smaller than the threshold value C is determined, if smaller, the rotational speed and the second speed of the output shaft 8 Since the rotation speeds of the main gear 9C for use in the vehicle are substantially synchronized, the route R ₂
Through the process proceeds to step S _7, after releasing the first clutch 5 and the second clutch 6, and sends a gear shift enable signal at step S _8.

If the difference between the target rotational speed NDT and the current rotational speed ND is larger than the threshold value C, the computer 22 controls the first clutch 5 to increase the rotational speed of the counter shaft 16 in step S ₁₃ . Operation is commanded.

That is, the computer 22 judges that the operation is a downshift operation, and the first clutch 5 is operated to operate the fluid pressure switching valve 58A to increase the rotational speed of the second speed main gear 9B. Compressed fluid is supplied to the first clutch 5, the piston is moved to bring the shaft side clutch plate 29 and the housing side clutch plate 30 into close contact, and the synchro shaft 3 is accelerated, and the second speed is set via the counter gear 25. The main gear 9C is accelerated to approach the rotation speed of the output shaft 8.

In the case of shifting to the third speed or the fourth speed, the increased rotation of the synchro shaft 3 is caused by the counter gear 25, the second speed main gear 9C, the second speed counter gear 19C, the counter shaft 16, the third speed or the fourth speed. High speed counter gear 19D,
The main gears 9D and 9E for the third speed or the fourth speed are accelerated via 19E to approach the rotation speed of the output shaft 8.

After returning to the point A through the route R ₃ , the same operation is repeated from step S ₁ until the rotational speed of the counter shaft 16 approaches the target rotational speed NDT.

If the target rotational speed NDT is smaller than the current rotational speed ND in step S ₉ , it is determined that the shift is an upshift, and the process proceeds to step S ₁₄ to calculate the change rate of the rotational speed difference with respect to time. To do.

[0063] Then the threshold B of the deceleration pattern in the current state from the graph of experimentally determined threshold value (FIG. 5) as a function of the temperature T of the change rate and the transmission oil to time the difference in rotational speed in Step S ₁₅ Ask.

[0064] Whether the difference between the current rotational speed ND of the target speed NDT and the counter shaft 16 is smaller than the threshold value B in step S ₁₆ is judged, if smaller, the rotational speed and the second speed of the output shaft 8 Since the rotation speeds of the main gear 9C for use in the vehicle are substantially synchronized, the route R ₄
Through the process proceeds to step S _7, after releasing the first clutch 5 and the second clutch 6, and sends a gear shift enable signal at step S _8.

If the difference between the target rotational speed NDT and the current rotational speed ND is larger than the threshold value B, the computer 22 operates the second clutch 6 to reduce the rotational speed of the counter shaft 16 in step S ₁₇ . Is ordered.

That is, the computer 22 determines that the operation is a shift-up operation, and the second clutch 6 is operated to reduce the rotational speed of the second-speed main gear 9B, so that the fluid pressure switching valve 58B is operated to release the compressed fluid. Second
To the clutch 6, and the piston is moved to bring the shaft side clutch plate 42 and the fixed clutch plate 41 into close contact with each other.

The fixed clutch plate 41 is attached to the shaft side clutch plate 42 rotating together with the synchronizing shaft 3 by the operation.
The braking force due to the frictional force with
The rotation speed of is reduced.

Then, the route R ₃ is returned to the point A, and the same operation is repeated until the rotation speed of the main gear changed from step S ₁ is synchronized with the rotation speed of the output shaft 8.

Further, the speed of acceleration or deceleration is such that when the computer 22 controls the pressure of the compressed fluid supplied to the first clutch 5 or the second clutch 6 to perform rapid acceleration / deceleration, a high pressure compressed fluid is used. When performing slight acceleration / deceleration, a relatively low pressure compressed fluid is supplied to accelerate or decelerate, so it is possible to accelerate or decelerate to a predetermined rotation speed in a short time. Can be done quickly.

Although the above embodiment has been described with reference to a so-called finger touch control type transmission, it is also applicable to a so-called automatic transmission.

[0071]

As described above, the present invention provides a first clutch and a synchro shaft for connecting or disconnecting the output gear and the synchro shaft, which are driven by the synchro gear fixed to the output shaft as described above, and a case of the transmission. A second clutch that connects or disconnects the gear, operates the first clutch to increase the rotational speed of the synchro shaft when the gear is downshifted, and operates the second clutch when the gear is upshifted. Since the rotation speed of the synchro shaft is reduced and the counter shaft is accelerated or decelerated through the counter gear and the main gear that are spline-fitted to the synchro shaft, the rotation speed of the main gear and the output shaft can be reduced in a short time. There is an effect that can be synchronized, and as a result, the driver's will The shift operation can be performed on Ri, it may Tekiru effect of increasing nimble driving performance.

Further, the target rotational speed of the counter shaft which allows the gear shifting operation from the number of teeth of the gear to be shifted and the current rotational speed of the output shaft, and the rotational speed difference between the target rotational speed and the current rotational speed of the counter shaft. The calculation is performed to determine the permissible range, and when the difference between the rotational speeds is within the permissible range, the transmission is caused to perform a gear shifting operation, so that a smooth gear shifting operation is performed without using a so-called conventional synchromesh mechanism. There is an effect that can be.

Further, the permissible range of the rotational speed difference is controlled using optimum values which are determined in advance from the rate of change of the rotational speed difference with respect to time for each acceleration pattern or deceleration pattern of the counter shaft and the temperature of the transmission oil. Therefore, there is an effect that a smooth gear shift operation can always be performed in either gear shift up or shift down operation.

[Brief description of drawings]

FIG. 1 is a side view showing an overall configuration of a shift control device of a transmission.

FIG. 2 is a schematic diagram showing a configuration of a shift control device.

FIG. 3 is a flowchart showing a routine of a shift control device.

FIG. 4 is a graph of threshold values when the output shaft is decelerated.

FIG. 5 is a graph of a threshold value when the output shaft is accelerated.

[Explanation of symbols]

DESCRIPTION OF SYMBOLS 1 Shift control device for transmission 5 First clutch 6 Second clutch 8 Output shaft 10 Constant mesh gear type transmission device 16 which is an example of transmission device 16 Counter shaft 22 Computer which is an example of control device 27 Case 50 Output shaft speed detection Device 51 Counter shaft rotation speed detection device 52 Oil temperature sensor 53 Gear position sensor

[Procedure amendment]

[Submission date] October 31, 1993

[Procedure Amendment 1]

[Document name to be corrected] Drawing

[Correction target item name] All drawings

[Correction method] Change

[Correction content]

[Figure 1]

[Fig. 2]

[Figure 4]

[Figure 5]

[Figure 3]

Claims (3)

[Claims] 1. A first clutch for connecting or disconnecting a counter shaft and an output shaft to accelerate the rotation of the counter shaft, and a counter clutch for connecting or disconnecting the counter shaft and a case of a transmission. A second clutch for decelerating the rotation is used to calculate a target rotational speed of the counter shaft that allows the speed changing operation from the number of teeth of the gear to be speed-changed and the current rotational speed of the output shaft. When the current rotation speed is lower than the target rotation speed, the first clutch is operated to accelerate the rotation of the counter shaft, and when the current rotation speed is higher than the target rotation speed, the second clutch is operated. To reduce the rotation speed of the counter shaft, A shift control method for a transmission, wherein a shift operation of the transmission is performed when a difference from the rotational speed becomes smaller than a predetermined value. 2. The predetermined value for enabling the speed change operation is determined in advance for each acceleration pattern or deceleration pattern of the counter shaft according to the rate of change of the rotational speed difference with respect to time and the oil temperature of the transmission oil. The shift control method for a transmission according to claim 1, wherein the shift control method is a set value. 3. A first clutch that connects or disconnects the counter shaft and the output shaft, a second clutch that connects or disconnects the counter shaft and the case of the transmission, and a rotational speed of the output shaft is detected. Output shaft rotation speed detection device, counter shaft rotation speed detection device that detects the rotation speed of the counter shaft, oil temperature sensor that detects the temperature of the transmission oil, and gear position that detects the transmission gear position selected by the gear shifting operation. The target rotation speed of the counter shaft that allows the shift operation is calculated from the sensor, the number of teeth of the gear selected by the shift operation, and the rotation speed of the output shaft, and the current rotation speed of the counter shaft is calculated as the target rotation speed. If it is less than the number, A control device that is activated to accelerate the rotation of the counter shaft, and that activates the second clutch to decelerate the rotation of the counter shaft when the current rotational speed is higher than the target rotational speed. A shift control device for a transmission having a feature.