JPH02271148A - Speed change controller - Google Patents

Abstract

PURPOSE:To prevent the breakage of a belt made of synthetic resin by controlling the pressurizing force between a belt and a pulley disc wheel and returning the belt to a prescribed speed change region, in slip, and applying the regular frictional force of the beet. CONSTITUTION:When a driving pulley 2 and a driven pulley 4 transmits a regular turning power, slip generation is little between a belt 5 and pulley disc wheels 21 and 22, and a strong frictional transmission state is generated by a speed change controller 60 as the second pressurizing means and the third pressurizing means 45, and speed change operation is carried out by a shifter 58. When power failure occurs, a shifter 51 is lowered by a motor 15, and the pressurizing for the speed change controller 60 is released, and the third pressurizing means 45 applied a weak frictional transmission force onto the disc wheel 22 of the pulley 2. When the pulley 2 is turned from this stator, power transmission is carried out with slip, and then the shifter 51 is raised by the motor 51, and if the pressurizing force of the speed change controller 60 is applied, the normal strong frictional transmission state is obtained, suppressing the starting impact. Thus, the long life of a belt can be secured.

Description

[Detailed Description of the Invention] [Industrial Application Field] The present invention provides a speed change that enables power transmission to be carried out normally from a predetermined rotation speed when starting a belt transmission using a variable diameter pulley. Regarding a control device.

[Prior art]

FIG. 6 shows a basic configuration diagram of a conventional belt transmission.

Fixed wheels 2a, 4a and a sliding type 2b are provided on the input shaft 1 and the output shaft 3, such as a rotating shaft of a prime mover, respectively.

A speed change boolean IJ 2 on the drive side A and a speed change pulley 4 on the driven side B are attached. Each of these speed change pulleys 2 and 4 has a pressure mechanism 6A, 6B, respectively.
Furthermore, sliding mechanisms 7A and 7B are provided. In this example, the pressure mechanism 6A is shown as a manual hoist and a bearing device, and the pressure mechanism 6B is shown as a spring. Sliding mechanism device 8A.

8B, and lubricating devices 9A and 9B consisting of lubricating oil seals and oil seals.

In the belt transmission 10 having this type of configuration, the sliding type 2b of the speed change pulley 2 on the driving side A is forcibly wound up and moved by a force that overcomes the spring 6B, and as a result, the belt 5 and the pulley 2 are moved.
Speed change control is performed by changing the contact radius with the

〔problem〕

In principle, this type of transmission exhibits constant torque characteristics or constant torque characteristics in the low speed range, so the target load equipment to which it is applied also has low speed characteristics in the low speed range, such as conveyors, agitators, centrifuges, and blowers. There are many horsepower devices. Therefore, when this type of load is targeted, high-speed startup requires high horsepower, and the instantaneous impact applied to the belt becomes extremely large, which accelerates damage to the belt core material. Therefore, if high-speed direct-on startup is repeated, belt breakage accidents are likely to occur in a short period of time.

For this reason, after the end of the exercise, the operator usually operates the manual handle 6A to a low speed range and then stops the input driving force.

However, the input power is often stopped inadvertently during speed change operation in a high-speed range due to operator error, power supply or oil supply to the prime mover being stopped, or the like.

At this time, the belt 5 stops at the high-speed control position as shown by the dotted line in FIG. 6, and as a result, the next time it is started, it is forced to start directly.

Further, as the belt 5 is held by the spring 6B of the pulley 2, even if the handle 6A on the pulley 1 side is operated to the low speed side, the belt 5 will not return to the original low speed range unless the pulley 1642 is rotating. Furthermore, even if rotational force is applied to the pulley 1 in this state, the belt 5 and the pulley 1 spin idly and do not transmit power, so there is also a drawback that recovery is not possible in this case.

〔the purpose〕

This invention was made in order to eliminate such drawbacks, and even when stopped at an arbitrary gear ratio, when starting, the gear ratio is returned to a different predetermined gear ratio position, and this position is restored. It is an object of the present invention to provide a speed change control device that can transmit load power from a vehicle to a vehicle.

Another object of the present invention is to provide a speed change control device that is improved so that the return operation can be performed not only manually but also remotely and automatically.

[Technical means for solving the problem] In order to achieve the former purpose, the present invention applies pressure by means of a first pressurizing means and a second pressurizing means having a larger operating force F2 than this pressurizing force F. A speed change control device for a transmission in which a belt is wound between the first and second pulley wheels being pressed, and the speed ratio is controlled by the second pressurizing means, in which the pressing force F is smaller than that of the first pressurizing means. and a third pressurizing force that applies the pressing force F to the sliding disc wheel of the second pulley wheel separately from the second pressurizing means when the operating force of the second pressurizing means is released. A pressure means is installed, and the second pulley wheel
Speed change control is performed so that the belt and disc wheel are kept in a strong friction transmission state while the pressure means is pressurizing, and only the third pressure means is rotated while being maintained in a weak friction transmission state during pressurization. This is an improved device. Also, to achieve the latter purpose,
A belt is wound between the first and second pulley wheels which are respectively pressurized by a first pressurizing means and a second pressurizing means having a larger operating force than the first pressurizing force, and the second pressurizing means is used to control the gear ratio. In the shift control device for a transmission that controls the first
It has a pressing force F3 smaller than that of the pressing means, and the second
When the operating force Ft of the pressurizing means is released, the pressing force F is applied to the sliding disc wheel of the second pulley separately from the second pressurizing means.
3 and further connected to the second pressurizing means, the second pressurizing means prevents rotation of the pulley wheel for a predetermined period of time when starting the transmission. The gear ratio control device includes a gear ratio controller including an initial return controller that starts the pulley wheel after forcibly shifting the gear ratio commanded by the means to an initial state.

[For production]

According to this invention, when transmitting input power, two types of transmission states can be obtained between the belt and the pulley disc: a strong friction transmission state and a weak friction transmission state. As a result, when supplying in a strong friction transmission state, it is used for regular crawling operation with the purpose of transmitting a predetermined horsepower of input power to the load, and when coupled in a weak friction transmission state, the input power is used normally. It is possible to return the belt to the position of a predetermined gear ratio while actively generating slip between the belt and the pulley disc, that is, while avoiding the starting impact applied to the belt.

Moreover, these operations are not limited to those performed by the operator manually operating the handle, but can also be performed by remote automatic control from a distance to return the belt to the predetermined gear ratio. It becomes possible to protect bearings, etc.

〔Example〕

A transmission control device according to an embodiment of the present invention will be described here using an example in which a transmission is controlled completely automatically.

FIG. 1 shows a schematic plan configuration diagram of a transmission to which a speed change control device of the present invention is applied. In the figure, the same symbols as in Figure 6 are
Since the same or equivalent parts will be shown, the explanation will be omitted. 10 is a transmission, 11 is a housing, and a transmission controller 60 as a second pressurizing means is moved in the direction of the arrow from the flange llb of the opening 11a, and the engagement between the shifter 58 and the support body 24 is released. It shows how it is separated and removed. At this time, the belt 5 is at the lowest speed position 5L. The speed change controller 60 includes an actuator 40 including a circuit section 30 and a control electric section 15, and a wrinkle section 50 to form a bar assembly 60.

FIGS. 2(A) and 2(B) are a partial sectional view and a plan view showing how the second pressurizing means 60 is fixed to the housing 11. FIG. In the figure, an electric motor 13 is installed in a housing 11, and a pulley wheel 20 is attached to its input shaft 12 in a cantilevered manner. The pulley wheel 20 is a completely oil-free centrifugal lubrication sliding mechanism (International Patent Application No., PCT
／Refer to issue) has been adopted.

The sliding portion 26 of the sliding circular mold 2z slides up and down with respect to the support shaft portion 25 of the fixed circular mold 21, so that the belt is held between the conical tapered portions of the respective circular temporary molds 21 and 22. (not shown) continuously changes the radius of the contact circumference with the circular molds 21 and 22 to control the speed change.

On the other hand, a support body 24 is fitted into the boss 26 of the sliding circular temporary mold 22 via a bearing 23, and a shifter 58 of a second pressurizing means 60 is separably connected below the buffer ring 27. .

In the circuit unit 30, a circuit device 34 is disposed on a base 33 in a room sealed with a casing 31 and a maintenance lid 32.

In the figure, 33 is a capacitor, 36 is a potentiometer, and a winding lead 37 is assembled thereto. A pair of limit switches 39a, 39b and an adjustment tool 37a for operating the switches are provided in the middle of the winding lead 37.

37b, a pair of gears 37c, 37d at one end, and a series of gears 38a, 38b at the other end. Furthermore, the frame 41 to which the control motor section 15 is attached is fixed to the casing 31 with screws 31a, and after the integral assembly,
A bolt 31c is fixed to the housing 11 through the through hole 31b. Further, the electric motor section 15 is composed of a frame 41 pressurized into a special shape, a gear head 16 and a reversible electric motor 15 installed thereon, and a gear 17.

The circuit section 3o and the motor section 15 configured in this way are connected to the gears 17, 18b, 18a, the winding door 37, the gears 37c, 37d, and the potentiometer 36.
The rotational power is transmitted to the shifter 58, which will be described later.
The actuator 40 for the wrinkled portion 50 is formed by detecting the displacement or speed ratio of the wrinkled portion 50 .

Next, the wrinkled part 50 includes a support frame 42 fixed to the back surface of the flat part 41b of the frame 41 by four screw parts 43,
The winding screw 54 installed inside it, and the oil
It is composed of a bus 57a, a through hole 56a, a guide shaft 57, and a shifter 51. This shifter 5I is formed into a 7-shape as a whole, and a through hole 56 in which a sealing member is installed is opened in the center of the shifter 5I, and a guide shaft 57 passes through the shifter 5I.

One end of the shifter 51 is screwed into a winding screw 54 via a bushing 53 which is internally threaded and has upper and lower grease retainers 53a and 53b. Further, the other free end portion is divided into two parts in a Y-shape or a U-shape, and an engaging end 58 is formed at the tip. Since the winding screw 54 is engaged with the gear 18 described above, the shifter 51 slides up and down on the guide shaft 57 according to the direction of rotation of the reversible electric motor 15, and the tip retaining end is at position 58'. The sliding circular temporary mold 22 is slid, thereby controlling the speed change.

Note that the U-shaped engagement end 58 of the shifter 51 is connected to the sliding pulley 2.
It is engaged with the support body 24 installed via the bearing 23 provided around the contact portion 26 of the second pressurizing means 60 so that the rotational power of the electric motor 15 is applied to the sliding circular temporary mold 22. Placed.

In this embodiment, a third pressurizing means 45 having a spring 44 is further assembled to the engaging end 58 of the shifter 5.

FIGS. 3(A) and 3(B) respectively show a front view and a sectional view of the third pressurizing means. In the figure, reference numeral 46 denotes a pressing lever, which is comprised of a guide portion 46a, a locking portion 46b, and a pressing portion 46'C, and is fitted into a through hole 59 of the shifter 51. Branch F
i, 48 are screwed together like both ends 47b, 4C of the two pillars 47a. It has a structure in which a lever 46 is fitted into a passage 48a.

Now, as shown in FIG. 5, the spring 44 has a pressing force F greater than that of the first pressurizing means, that is, the spring 6B.
It has a much smaller pressing force F3. The second pressurizing means, that is, the speed change controller 60 applies the operating force F2 for speed change control to the sliding circular temporary mold 22, which is the pressing force F2 of the driven pulley wheel 4.
, so in the end the three acting forces have F 3 <
There is a relationship of F + < F z.

Therefore, while the pulley wheels 2 and 4 are normally transmitting rotational power, the belt and the pulley disks are in a so-called strong friction transmission state in which slip occurs very little. Therefore, at this time, the acting forces F+ and F of the first and second pressurizing means
The operation is determined by the relative relationship of z. That is, F in the transmission of this embodiment.

When < F t, the speed increases, and when Fz <F, the speed decreases. At this time, the pulley wheel rotates 2.4 times, so both acting forces are applied to the belt 5, but the pressing force F3
is selected to be about 175 to 1710 from F. As a result, during this normal transmission operation, the third pressurizing means 45 does not work, and the thrust support 24 of the sliding circular mold 22 is in close contact with the shifter tip 39 as shown in FIG. 3(C). , furthermore the second
A normal speed change operation is performed between shifters 58 and 58' indicated by dotted lines in FIG.

Next, as in the case of a power outage, the pulley wheel 2 is
state (that is, the belt 5 is at the dotted line position 1Z5 in Fig. 1).
The operation when stopped in H state) will be described. At this time,
When the pressure of the second pressurizing means, that is, the speed change controller 60 is released by manual or automatic operation, the shifter 51 begins to move downward. Since the belt 5 has already stopped, the acting force F of the first pressurizing means 6B.

is blocked. As a result, the shifter 51 is moved and the second
When the pressure of the pressurizing means 60 is released, the third pressurizing means 45 applied to the shifter tip 58 is applied to the disc type 22 of the pulley wheel 2 independently of the second pressurizing means 60. FIG. 3(D) shows this situation. At this time, the third pressurizing means 45
As the shifter 51 operates, the loft 46 as shown in FIG.
The only part protrudes and applies a pressing force F3 to the disk mold 22.

When input power is applied to the input shaft 2 and the pulley wheel 2 is rotated from the state shown in FIGS. 3(B) and 3(D), a pressing force F is applied between the belt discs of the drive pulley wheel 2.

is small, normal power transmission does not take place, resulting in weak frictional transmission. On the other hand, the driven pulley wheel 4 has the first pressurizing means 6
B is in a state of strong friction transmission, but when input power is applied in this state, the belt disc wheel slips on the pulley wheel 2 side, transmitting power little by little irregularly, and the belt 5 stops rotating. Since the relationship between the starting forces of 0 and 0 is F3 (Fl), the sliding circular mold 22 of the drive pulley wheel 2 is
It returns to the position indicated by the dotted line in Figure (D) in a short period of time.

If the second pressurizing means, that is, the acting force F2 of the transmission control device 60 is energized after this return, substantially at the time of startup,
It is possible to avoid the starting impact on the belt 5 due to the high-speed direct insertion state. As a result, it can be used not only as a start-up measure in the event of a power outage, but also as a soft starter (slow start) means during normal operation.

FIGS. 4(A) and 4(B) show control circuit diagrams of an embodiment including a speed ratio controller when the above-mentioned speed change control device is fully automated.

In the same figure (A), the gear ratio control circuit CC is connected to the power circuit PW for the main motor 13. MCB is a breaker, MG is a magnet, To and T1 are both timers, and 1x to 4x are relays. SQ is a relay sequence circuit consisting of an initial and final return circuit. DL is an instantaneous power failure prevention circuit consisting of a rectifier smoothing circuit and a delay circuit. Further, D is a remote activation switch. In this embodiment, the PC is a temperature controller TPC and a resistance temperature detector 1? This is an adjustment circuit composed of a TD and a second pressurizing means 60.

FIG. 4<8) is a sequence diagram illustrating the operation of the control circuits cc and p-. Here, as shown in FIG. 3(A), an example of the return operation is shown when the belt 5 in the drive-side pulley wheel 2 stops at the high-speed control position.

In the same figure, starting switch D is turned on and L
), the case where the transmission 10 is turned on and off by the breaker MCB will be explained as an example. If the breaker is not turned on, the situation is the same as a power outage. At this time, when breaker MCB is turned on as shown in Figure (i), timer T is activated via instantaneous power failure prevention circuit DL.

is turned on and starts counting the time, but until the count up as shown in Figure (1■), the contact of timer TO is open, magnet MG is not energized, and the b contact is between deceleration command terminal PA + P1 of controller TPC. Since the controller T
A forced deceleration command is supplied from PO to the second pressurizing means 60 through terminal C1. Therefore, since the main motor 13 is stopped, the pulley wheel 2 is also stopped, and only the shifter of the speed change controller 60 is operated to the low speed side as shown in FIG. As a result, the shifter 51 is in the state shown in FIG. 3(D). Here, when the timer To times up, the contact To is closed and the controller TPC supplies a normal control output to the second pressurizing means 60.

Therefore, even if a speed increase command is issued from the controller TPC at this time, the belt 5, which was in the high speed position as shown in Fig. 3(C), will move to the low speed position (as shown in Fig. 3(C)) in an extremely short period of time. During this time, the shifter 51 of the second pressurizing means 60 moves only slightly at a slow rate, so there is no effect. Therefore, as shown by the solid line in Figure (V), after the belt 5 moves to the low speed state (A) within a short time, the controller T
It ascends to the control position (b) of the PC and performs adjustment operations such as well-known planting control or program control operations.

Next, the operation when the starting switch D is closed as shown in FIG. 2(i) will be described.

At this time, relay 1x dissipates heat, but relay 2χ.

3x continues to be energized, and the second timer T1 is activated as shown in figure (V).
starts counting and relay 4X is turned on. The result diagram (
As shown in vi), the controller TPC supplies a forced deceleration command to the second pressurizing means. At this time, unlike the case of the initial return circuit described above, the pulley wheels 2 and 4 are rotating, so the second
The shifter 5I of the pressurizing means functions in deceleration operation from the dotted line position to the solid line position in FIG.
Pressure means do not work. The timer T may be set to be larger than the time required for the shifter 51 to descend from the high speed position to the low speed position. When timer T+ counts up, relays 2X, 3X and magnetic contactor MG are deenergized.
The transmission 10 also stops in the lowest state. Therefore, at the next startup, a soft start operation can be performed without the sequence of the initial return circuit operating.

Note that the configurations shown in FIGS. 1 to 3 do not require automatic control as shown in FIG. 4, and the actuator 40 may be configured to be manually operated using a gear, a handle, or the like.

Furthermore, when the speed change controller 60 shown in FIG. 3(C) is attached to and removed from the transmission as shown in FIG. Engagement becomes difficult again. Therefore, in this embodiment, a locking hole 49 is formed in the rod 46 in advance. When removing the controller 60, remove the lid 11. of the transmission 10. a is removed, the pin 49a is passed through the locking hole 49, and the operation of the loft 46 is locked.

FIGS. 5(A) and 5(B) show that the transmission controller 60 is connected to the transmission 1.
FIG. 6 is a side view and a bottom view of a locking device W61 for attaching and detaching the lid 11a without opening the lid 11a when separating from the locking device 0.

In the figure, the same reference numerals as in FIG. 3 indicate the same or corresponding parts. Lot 46 has a D cut on the left and right, and the left side 65a
The right side 65b acts as a locking portion with the locking blade 62. The blade 62 also has two support parts 63.
a and 63b, and a spring 64 always engages the right side D cut 65b to lock the movement of the rod 46. On the other hand, an abutting body 67 is erected at one end of the blade 62, and the tip of the rod 66 abuts against this abutting body 67. The rod 66 is configured to be screwed into a tap provided on the panel 33, as shown by a broken line 66 in FIG. 2(B). Therefore, when the screw is completely screwed, the blade 6
The locking portion 64 of No. 2 and the right D cut 65b of the rod 46 are released, and the rod 46 performs a normal pressurizing operation. When attaching and detaching the controller 60 to the transmission 10, use the bolts 6
All you have to do is release the screw 6.

In this gear ratio controller CC, the gear ratio of the second pressurizing means is:
Although the example has been explained with three types of initial return operation, final return operation, and further intermediate adjustment operation, the final return operation is omitted.
It is also possible to use the normal soft start function only in the case of an initial recovery operation other than during a power outage.

In addition, when the rising and falling speed of the shifter 51 is fast, the return timing period T shown in FIG. 4(B) (V),
During this period, the operation of the second pressurizing means 60 may be suppressed using a timer or the like, and a person skilled in the art can easily do this.

(Other Embodiments) In the present embodiments, the case where the gear ratio is controlled using the shifter arm 51 has been described as an example, but there is no reason to be limited to this.

For example, a speed change control system in which the first and second pressurizing means are hydraulically driven is also known, but hydraulic pressure may be used instead of a spring as the third pressurizing means. In addition, the three acting forces F, F, which have been mentioned above as a control method.

P during F3! <F! < F z is maintained, and if the acting force F of the third pressurizing means is large enough to return the belt to the desired position while actively generating slip. For example, the pressure of the same hydraulic mechanism may be changed.

〔Effect of the invention〕

According to the present invention, even when the belt of the transmission is stopped at an arbitrary position, regular rotational power can be transmitted to the load at the desired rotational speed at the time of startup. This means that, for example, in equipment where the required output increases as the speed goes up, or a load with a large moment of inertia, if direct operation is performed from the high speed range at startup, the belt will be damaged in a short period of time. However, according to the present invention, by controlling the pressing force between the belt and the pulley disc type, the belt in the high speed range is actively caused to slip while returning to the low speed range, and the normal belt friction thereafter is maintained. Since normal power transmission operation is resumed by applying force, the synthetic resin belt is not damaged and its service life can be extended.

Furthermore, since the operation of changing the belt speed position actively utilizes the slip between the belt and the pulley, unlike conventional methods, clutches are installed individually on the input and output shafts, and the clutches are placed in a preload state. Compared to the case where the belt is relocated, the equipment is cheaper and maintenance is simpler. This is particularly effective in large-capacity transmissions, which extends belt life and improves device reliability, and also allows for slow startup operations or during power outages.
As a recovery measure in the event of an emergency accident, it can be fully automated by simply adding sequences such as computer software, which has the advantage of significantly expanding the range of industrial applications.

[Brief explanation of drawings]

FIG. 1 is a schematic plan view of a transmission to which a speed change control device according to an embodiment of the present invention is applied, and FIGS. Cross-sectional view, plan view, Figure 3 (A)
, (B) are a full view and a sectional view of the third pressurizing means used in the same embodiment device, respectively, and FIGS. 3(C) and (
D) is an explanatory diagram of the operation when the same means is connected to a pulley wheel, and Figures 4 (A) and (B) are diagrams showing how the speed change controller shown in Figures 2 (A) and (B) is automatically operated. The electrical wiring diagram and sequence operation diagram for control are shown respectively, and Fig. 5 (A)
, (B) shows a configuration diagram of the locking mechanism applied to the embodiment device of FIGS. 2 and 3. Furthermore, FIG. 6 shows a sectional view of a conventional transmission. 2... Drive pulley wheel, 2a, 21... Fixed disc wheel,
2b, 22...Sliding disc type, 4...Driven pulley wheel,
4a...Fixed disc wheel, 4b...Sliding disc type, 5...
・Belts 6A, 60...Second pressure means or speed change controller, 6B...First pressure means or spring, 10.
...Transmission, 15... Control transmission section, 30... Circuit section, 40... Actuator, 50... Shifter section, 5
1...Shifter patent applicant Tokyo Jidokiko Co., Ltd. Straw 1 Figure "+"-1+1 -ichino, --no--T-1 Figure 4 (B) Procedural amendment book 1981! February 25th 1, Display of the case 1988 Patent Application No. 134,439 2, Name of the invention Transmission control device' + h0 Relationship with the case Patent applicant address Name 5, Amendment order Date: November 28, 1999 (shipment date) 8, Contents of the amendment Figure 6 in the middle of the drawing (please refer to the attached sheet 1T for the fact that it is in B.) 62 bjal bjD inkstone

Claims (21)

[Claims] (1) A belt is wound between the first and second pulley wheels which are respectively pressurized by the first pressurizing means and the second pressurizing means having an operating force F_2 larger than the pressurizing force F_1, and the belt is wound between the first and second pulley wheels. In a speed change control device for a transmission in which a gear ratio is controlled by a pressure means, the pressure force F_3 is smaller than the first pressure means, and when the operating force of the second pressure means is removed, the second pressure is applied. Separately from the means, a third pressurizing means for applying the pressing force F_3 to the sliding disc wheel of the second pulley wheel is installed, and the second pulley wheel applies the pressing force F_3 to the sliding disc wheel of the second pulley wheel. A speed change control device in which the belt and disc wheel are kept in a strong friction transmission state during pressurization, and only the third pressurizing means is rotated while maintaining a weak friction transmission state during pressurization. (2) The speed change control device according to claim 1, wherein the third pressurizing means is formed of a spring that constantly pressurizes the sliding disc wheel of the second pulley wheel. (3) The speed change control device according to claim 2, wherein the second pressurizing means is constituted by a hydraulic pressurizing mechanism connected to the second pulley wheel. (4) The speed change control according to claim 2, wherein the second pressurizing means is a speed change controller comprising a wrinkle connected to the second pulley wheel and an actuator that applies an operating force to the wrinkle. Device. (5) The speed change control device according to claim 4, wherein the spring is arranged between a support provided on the sliding disc wheel via a bearing and the wrinkle. (6) The speed change control device according to claim 5, wherein the third pressurizing means includes the spring and a press lever that is constantly pressurized by the spring. (7) The third pressurizing means is integrally attached to the support body or the wrinkles, and the support body and the wrinkles are configured to be able to engage or separate from each other. The speed change control device described in . (8) The second item pressurizing means, which is the transmission controller, is located at a position where the wrinkle and the support body engage when the wrinkle and the actuator are integrally assembled and fixed to the transmission housing. 8. The speed change control device according to claim 7, wherein the wrinkles are arranged. (9) The speed change control device according to claim 8, wherein the actuator of the second pressurizing means, which is the speed change controller, has a speed ratio controlled by manual operation from outside the housing. (10) The actuator of the second pressurizing means, which is the speed change controller, has a reversible control transmission for energizing the wrinkles, and the speed ratio is automatically controlled.
The speed change control device described in . (11) The third pressurizing means is provided with a locking mechanism that prevents the third pressurizing means from supplying an operating force when the second pressurizing means is attached or detached from the transmission main body. A speed change control device according to claim 12. (12) A belt is wound between the first and second pulley wheels which are respectively pressurized by the first pressurizing means and the second pressurizing means having an operating force F_2 larger than this pressurizing force F_1, and In a speed change control device for a transmission that controls a gear ratio using pressure means, a pressing force F_3 smaller than the first pressure means described above.
Moreover, when the operating force F_2 of the second pressurizing means is released, a third pressurizing force F_3 is applied to the sliding disc wheel of the second pulley wheel separately from the second pressurizing means. A speed change ratio that is connected to the pressurizing means and the second pressurizing means and commanded by the second pressurizing means by preventing rotation of the pulley wheel for a predetermined period of time when starting the transmission. A speed change control device comprising a speed ratio controller including an initial return controller that starts the pulley wheel after forcibly moving the pulley wheel to an initial state. (13) Claim 12, wherein the initial state of the gear ratio commanded by the second pressurizing means is a low speed state, and the initial return controller is a sequence controller for returning to the conventional state. The speed change control device described. (14) The speed change control device according to claim 13, wherein the third pressurizing means is formed of a spring that constantly pressurizes the sliding disc wheel of the second pulley wheel. (15) The second pressurizing means is a speed change controller comprising a wrinkle connected to the second pulley wheel and an actuator that applies an operating force to the wrinkle. Gear shift control device. (16) The speed change control device according to claim 15, wherein the third pressurizing means is arranged between a support member provided on the sliding disc wheel via a bearing and the wrinkles. . (17) The third pressurizing means is formed of the spring and the pressing lever, is assembled integrally with the wrinkle, and is removably fixed to the transmission housing. transmission control device. (18) The transmission control device according to claim 13, wherein the sequence controller is connected to a start switch of the transmission and causes the transmission to be soft-started by the sequence controller. (19) The gear ratio controller is connected to power failure detection means for power supply to the transmission, and operates the sequence controller when a power failure occurs.
The speed change control device described in . (20) The power failure detection means of the speed ratio controller includes a filter that prevents the sequence controller from operating when a momentary power failure occurs in the power supply.
The speed change control device described in . (21) The gear ratio controller includes an off-delay controller that rotates and forcibly moves the transmission to a low speed state for a predetermined period of time when the transmission is stopped, and then stops the transmission. A speed change control device according to claim 19 or 20.