JPH0715309B2 - Automatic synchronizer of gear type transmission - Google Patents

Description

Description: TECHNICAL FIELD The present invention relates to an automatic gear type transmission that automatically synchronizes the rotation of an output shaft and a counter shaft during gear shift gear conversion of a gear type transmission. Regarding a synchronizer.

[Prior Art] Generally, the gear type transmission has an output shaft for supporting a plurality of gears for speed change, and an auxiliary shaft, and an engine or the like transmitted to the auxiliary shaft via an appropriate clutch means. The rotational power from the outside is transmitted to the output shaft by the selective meshing of the gears to obtain the required gear shifting power. To make such a gear type transmission into an automatic transmission, the clutch means is used. One of the important issues is how to synchronize the rotations of the output shaft and the auxiliary shaft when the gear is once opened and the selection of the gear is changed.

Heretofore, as a conventional method for synchronizing the rotation of the output shaft and the auxiliary shaft at the time of changing the gear selection of such a gear type transmission,
In the neutral state of the transmission (the state in which the clutch means is opened) as shown in Japanese Patent Application Laid-Open No. 58-37357, "Transmission method and device of parallel shaft gear type automatic transmission", Based on a so-called double clutch action in which the auxiliary shaft is brought into the synchronous rotation range by repeating opening and closing (intermittent), and as seen in the title "Automatic transmission" of JP-A-59-180144.
A so-called double clutch that provides clutch means dedicated to the rotation of the auxiliary shaft to bring the auxiliary shaft into the synchronous rotation range, or rotation on the auxiliary shaft as seen in the title "Transmission" of JP-A-59-183152. Proposals have been made for utilizing a so-called dynamo, in which a drive means (dynamo) is provided to reduce or accelerate the inertial rotation of the sub shaft to bring the sub shaft into the synchronous rotation range.

[Problems to be solved by the invention]

Although it is possible to achieve some degree of rotation synchronization between the output shaft and the auxiliary shaft by the above-mentioned methods, the rotation of the auxiliary shaft is independent of the rotation of the output shaft. Even if temporary rotation synchronization can be achieved between the output shaft and the auxiliary shaft, it is not possible to maintain the consistency of the synchronized rotation arrival range. That is, the arrival of the auxiliary shaft in the synchronous rotation range is only transient.

In addition, in each of the above methods themselves, 1) based on the double clutch action, the control system for realizing the above-mentioned clutch operation becomes complicated.

2) With the double clutch, the size of the clutch portion is naturally increased, and the reliability of the clutch control remains a problem in reproducing the clutch control in a certain manner.

3) When a dynamo is used, the problem does not occur so much when the transmission is used in a relatively small vehicle, but when the transmission is used in a large vehicle having a large inertia, A dynamo with a large power generation capacity for decelerating or speeding up the rotation of the auxiliary shaft is required to overcome the inertia, and there remains a problem in terms of versatility.

It has some practical inconveniences.

In view of such a conventional situation, the present invention aims to synchronize the rotation of the output shaft and the auxiliary shaft when the gear selection is changed,
It is an object of the present invention to provide an automatic synchronizer capable of achieving both quick reaction of a counter shaft to a synchronous rotation range and reliable alignment and maintenance of the counter shaft in the synchronous rotation range.

[Means for solving problems]

In the present invention, the gear ratio is controlled by receiving the rotational power of the output shaft and controlling the inertial rotational speed of the output shaft to synchronize the rotational speed of the auxiliary shaft when the clutch means is opened. And a second clutch means separate from the clutch means that is closed when the clutch means is opened and transmits the shift output of the continuously variable transmission means to the sub shaft. The rotation of the output shaft and the auxiliary shaft should be synchronized when the gear selection is changed.

[Action]

By the continuously variable transmission means, the rotational speed of the auxiliary shaft to be synchronized with the rotational speed of the output shaft during inertial rotation is set at any time and should be synchronized with the set output shaft inertial rotational speed. The rotation speed is rapidly transmitted to the counter shaft through the second clutch means. Therefore,
After the clutch means (first) is opened, the rotation of the counter shaft is quickly synchronized with the rotation of the output shaft, and the output shaft of the counter shaft is controlled by the gear ratio control for the continuously variable transmission means. A good synchronization match will be maintained.

〔Example〕

FIG. 1 shows an embodiment of an automatic synchronizer according to the present invention.

As shown in FIG. 1, the synchronizer of this embodiment is a transmission that receives the rotational power of the engine 10, which is a power source, via the first clutch 20 and changes the speed thereof. The rotational power transmitted via 20 is further transmitted to the gear 31a.
And a first transmission gear group 33a composed of a counter shaft 32 transmitted via 31b and a plurality of speed change gears supported by the counter shaft 32.
And a second speed change gear group 33b composed of a plurality of speed change gears that are normally meshed with the respective gears of the first speed change gear group 33a, and selectively move based on an appropriate selection command given from the outside ( The mechanism for this movement by the electro-hydraulic actuator is not shown), and the combination designated at any time is selected from the combination of gears having different gear ratios in the first and second gear groups 33a and 33b. The output shaft to which the transmission power based on the combination (meshing) of the dog clutch 33c and the gear selected by the dog clutch 33c is finally transmitted as the transmission output of the transmission.
The rotation power (shift power) of the output shaft 34 via the gears 40a and 40b to the known gear type transmission 30 having
Is transmitted to the input shaft 51 and a first pulley 52 supported by the input shaft 51 and having a pulley diameter that changes according to a control described later as shown by an arrow in the drawing and a V stretched between the first pulley 52 and the first pulley 52. The rotational power is transmitted via the belt VT, and the second pulley 53 whose pulley diameter changes as shown by an arrow based on the control described later similarly to the first pulley 52 and the second pulley 53 supporting the second pulley 53. A continuously variable transmission 5 including an output shaft 54 to which speed change power of the rotational power of the input shaft 51 determined by the pulley diameters of the first and second pulleys 52 and 53 is transmitted.
0, the output shaft 54 of the continuously variable transmission 50 and the gear type transmission 30
A second clutch 60, which is arranged between the auxiliary shaft 32 and the auxiliary shaft 32 as shown in the figure, for controlling transmission / interruption of the transmission power of the output shaft 54 to the auxiliary shaft 32 based on a control described later, is arranged in an operating portion (not shown). A gear shift position sensor 71 for electrically detecting the gear shift position commanded by the gear shift command shift lever SF and whether the command is upshift or downshift,
For example, a first rotation speed sensor 72 of an electromagnetic pick-up type that detects the rotation speed of the output shaft 34 of the gear transmission 30 and a rotation speed of the auxiliary shaft 32 of the gear transmission 30 are detected. A second rotation speed sensor 73 of electromagnetic pickup type,
The continuous rotation speed of the output shaft 54 of the continuously variable transmission 50 is detected at any time. The third rotation speed sensor 74, which is also an electromagnetic pickup type, and the second clutch 60 are closed / opened as described above. The auxiliary shaft of the shifting power of the gear transmission output shaft 54
For example, a photoelectric clutch position sensor 75 for detecting the transmission / disconnection state to 32, and an input circuit 76 for receiving the detection outputs of these sensors 71 to 75 and performing necessary processing such as analog / digital conversion on each of them. The input / output pulleys 52 and 53 of the continuously variable transmission 50 capable of synchronizing the rotation speed of the auxiliary shaft 32 of the gear type transmission output shaft 34 at each shift position detected by the shift shift position sensor 71 with the auxiliary shaft 32. For each pulley diameter, the basic control values are detected by the sensor 71. The memory 77 including a ROM or the like which is stored in advance as a data table for each of the shift-up and shift-down of the shift command, and the input circuit 76. By looking up the memory 77 based on the detection data of the shift shift position sensor 71 added from This control value is read out from this, and the closing / opening setting of the second clutch 60 and the pulley diameters of the pulleys based on the detection data of the above-mentioned sensors, including the shift shift position sensor 71, which are added from the input circuit 76. An arithmetic circuit 78 for integrally controlling the operation of a hydraulic circuit, which will be described later, relating to setting and correction, and the arithmetic circuit
An output circuit 79 for performing required processing such as digital / analog conversion on the control data output from 78 and giving the processed data to the following hydraulic circuit, and a second control for switching the closing / opening of the second clutch 60. 1 hydraulic actuator 8
1. A second hydraulic actuator 82 for variably controlling the pulley diameter of the input pulley 52 of the continuously variable transmission 50, and a third hydraulic actuator for variably controlling the pulley diameter of the output pulley 53 of the continuously variable transmission 50. 83, and the strokes of the first to third hydraulic actuators 81 to 83 are individually controlled by increasing or decreasing the flow rate of oil supplied from the pump 80 based on the electric control signals applied from the output circuit 79. It is configured to include three solenoid valves 84 to 85 and 86, respectively. Note that, in FIG. 1, for convenience, the coupling mode of the hydraulic circuit is shown by a solid line, and the coupling mode of the electric circuit is shown by a broken line.

The operation of the synchronizing apparatus of this embodiment will be described in detail below with reference to the flowchart of FIG.

Now, one set of gears in the first and second speed change gear groups 33a and 33b are selectively meshed to operate (operation).
It is assumed that a command to change (shift) the selection of the gears is given to the gear type transmission 30 which is in the state through the shift command shift lever SF (the configuration for this is well known. The input circuit 76 informs the input circuit 76 of the fact that the shift command is issued through the shift shift position sensor 71 arranged on the shift lever SF and the shift contents (shift position and shift up position).
The shift down) is received, the digital signal is appropriately converted into a digital signal, and then transmitted to the arithmetic circuit 78 (step S1 in FIG. 2).
reference). When the shift command is issued, the first clutch 20 is once opened, and the gear transmission 30 in question is in a neutral state. Further, during this period, the continuously variable transmission 50 is driven by the inertial rotation of the output shaft 34 of the gear type transmission 30 in the neutral state (second clutch).
60 is still open at this point).

When the shift command and shift contents are applied to the arithmetic circuit 78 in this manner, the arithmetic circuit 78 looks up the memory 77 and determines the pulley diameters of the continuously variable transmission input / output pulleys 52 and 53 corresponding to the shift contents. The control value is read from the memory 77, and an electric signal corresponding to the read pulley diameter value is given to the solenoid valves 85 and 86 via the output circuit 79 (see step S2 in FIG. 2). This allows the solenoid valve 85
And 86, the pulley diameters of the corresponding pulleys are set and controlled through the hydraulic actuators 82 and 83, respectively, so as to correspond to the read pulley diameter values.
(See step S3 in the figure). By the way, if the content of the above-mentioned shift indicates "downshift", the input pulley among the above pulleys
The pulley diameter of 52 is made large, and the pulley diameter of the other output pulley 53 is made small so as to increase the rotation speed of the output shaft 54. The reverse is true for "shift pulleys".

When the setting control of the pulley diameter is completed in this way, the arithmetic circuit 78 then gives a command to the first electromagnetic valve 84 to close the second clutch 60 through the first hydraulic actuator 81, and thereby the first solenoid valve 84 is closed. The second clutch 60 is closed, and it is confirmed whether or not the closing control of the second clutch 60 is completed based on the detection output of the clutch position sensor 75 applied through the input circuit 76 (FIG. 2). See step S4). By closing the second clutch 60 in this manner, the auxiliary shaft 32 of the gear type transmission 30 receives the inertial rotational power of the output shaft 34 as drive power (input power), and thus the continuously variable transmission 50. It receives the shift output of and rotates to follow it.

When it is confirmed that the second clutch 60 is closed, the arithmetic circuit 78 further compares the detected output of the first rotational speed sensor 72 and the detected output of the second rotational speed sensor 73 applied through the input circuit 76. It is searched whether the rotational speed (rotational speed) of the output shaft 34 of the gear type transmission 50 and the rotational speed (rotational speed) of the auxiliary shaft 32 match (synchronize) (step in FIG. 2).
S5), when the rotation of these axes is not synchronized, the control signals applied to the solenoid valves 85 and 86 are appropriately changed while monitoring the detection outputs of the sensors 72 and 73. The pulley diameters of the input / output pulleys 52 and 53 are set through the hydraulic actuators 82 and 83 so that the detection output of the sensor 72 is matched with the detection output of the sensor 73 (so that the rotation of the auxiliary shaft 32 is synchronized with the rotation of the output shaft 34). Correction control is performed (see step S6 in FIG. 2). In the pulley diameter correction control, it is of course possible to correct only one of the pulley diameters 52 and 53.

If it is confirmed that the output shaft 34 and the auxiliary shaft 32 are rotationally synchronized with each other (step S5 in FIG. 2), finally, in the arithmetic rotation 78, the second clutch 60 is opened through the first hydraulic actuator 81. A command is given to the solenoid valve 84 to open the second clutch 60, and based on the detection output of the clutch position sensor 75 applied through the input rotation 76 as in the previous closing control, the second clutch 60 is opened. It is confirmed whether or not the opening control for 60 is completed (see step S7 in FIG. 2).

By opening the second clutch 60 through the above process, the auxiliary shaft 32 of the gear type transmission 30 inertially rotates at a rotational speed (rotational speed) synchronized with the inertial rotation of the output shaft 34. Become. Therefore, the subsequent gear transmission 30
The well-known speed change operation by gear shift in the inside can be achieved very smoothly. The output shaft 54 of the continuously variable transmission 50
The third rotation speed sensor 74, which is arranged in a portion and detects this rotation speed, performs the above-described pulley diameter setting control (step S3 in FIG. 2) and the closing control of the second clutch 60 (FIG. 2). It is used to confirm whether or not each desired control is achieved in step S4), and the detection output thereof is taken into the arithmetic circuit 78 and appropriately referred to in each of these controls.

As described above, according to this embodiment, the gear transmission
According to the inertial rotation of the transmission output shaft 34 when 30 is in the neutral state, the synchronous rotation of the transmission auxiliary shaft 32 can be promptly and forcibly controlled. Moreover, these output shaft 34 and counter shaft 32
Since the synchronous mode is closed-loop controlled on the basis of the detection of the respective rotational speeds, the synchronous matching between these axes is also well maintained.

It should be noted that the type of each sensor used in the apparatus of the above-described embodiment is arbitrary, and any other type can be used as long as it can achieve this with a function equivalent to the above for detecting the position or rotation speed of the detection target. It may be a sensor.

Further, in the apparatus of the embodiment, after the pulley diameter setting control and the second clutch 60 are closed, the pulley diameter is finely adjusted and corrected, and the output shaft 34 and the auxiliary shaft 32 of the gear type transmission 30 are connected. However, if the synchronization control can be achieved with a sufficient accuracy that can be achieved only by the pulley diameter setting control, the subsequent pulley diameter (after the second clutch 60 is closed) The correction control about can be omitted.

Further, in order to perform such pulley diameter setting control, the above-described embodiment realizes the same control by reading out the data corresponding to the gear shift command content from the data regarding the pulley diameter registered in the memory 77 as a data table in advance. However, in addition to this, for example, the data related to the above-mentioned gear shift command and the data related to the respective rotational speeds of the output shaft 34 and the auxiliary shaft 32 are simultaneously taken in, and these data and various known data necessary for the pulley diameter control are also acquired. Of course, the desired pulley diameter may be obtained by each calculation based on the hydraulic circuit constant or the like.

Further, in the apparatus of the embodiment, the case where the present invention is applied to the gear type transmission 30 having the structure shown in FIG. 1 is shown as an example, but the structure of the gear type transmission itself to which this invention is applied is It is optional. In short, it has an output shaft and a counter shaft that support a plurality of gears for shifting each other, and outputs the rotational power from the outside transmitted to the counter shaft through an appropriate clutch means through the selective meshing of the gears. Any structure may be used as long as it has a structure for transmitting to the shaft.

〔The invention's effect〕

As described above, according to the present invention, it is possible to quickly and accurately synchronize the rotation of the output shaft and the auxiliary shaft when the gear type transmission is in the neutral position, and to make the gear shifting operation of the transmission extremely smooth. be able to.

[Brief description of drawings]

FIG. 1 is a block diagram showing a configuration of an embodiment of an automatic synchronizing apparatus according to the present invention, and FIG. 2 is a flow chart showing an operation example of the embodiment synchronizing apparatus. 30 ... Gear type transmission, 32 ... Secondary shaft, 34 ... Output shaft, 50 ... Continuously variable transmission, 52, 53 ... Pulley, 60 ... Clutch, 71 ... Shift position sensor, 72, 73, 74 ... Rotation speed sensor , 75 ... Clutch position sensor, 76 ... Input circuit, 77 ... Memory, 78 ... Arithmetic circuit,
79 ... Output circuit, 80 ... Pump, 81, 82, 83 ... Hydraulic actuator, 84, 85, 86 ... Solenoid valve.

Continuation of the front page (56) References JP-A-58-37357 (JP, A) JP-A-59-180144 (JP, A) JP-A-59-183152 (JP, A)

Claims (2)

[Claims] 1. An output shaft and a counter shaft for supporting a plurality of gears for shifting each other, and rotational power from the outside transmitted to the counter shaft via a first clutch means is selected from the gears. Rotation of the output shaft and the auxiliary shaft when the selection of the gear is changed by opening the first clutch means of the gear type transmission for transmitting the transmission power to the output shaft by mechanical meshing. In an automatic synchronizer for a gear type transmission that synchronizes, when the rotational power of the output shaft is received and the first clutch means is opened, the rotational speed of the auxiliary shaft becomes equal to the inertial rotational speed of the output shaft. A continuously variable transmission means for controlling a transmission ratio to a synchronized ratio; and a second transmission means for closing the first clutch means when the first clutch means is opened and transmitting the shift output of the continuously variable transmission means to the counter shaft. A gear-type transmission equipped with a clutch means. Synchronization of the device. 2. The continuously variable transmission means is configured to preset and control the speed change ratio before the second clutch means is closed based on the content of the selection of the gear at any time, and the second clutch means operates. After the closing, the speed ratio is corrected and controlled so that the rotation speed of the auxiliary shaft matches the rotation speed of the output shaft based on the detection of the rotation speeds of the output shaft and the auxiliary shaft. ) An automatic synchronizing device for a gear type transmission according to the item.