JPS63275846A - Belt non-stage transmission - Google Patents

Abstract

PURPOSE:To improve the variation performance of the radius of a belt winding surface with a simple structure and a little controlling energy by controlling the sliding of a movable cone plate with a servo mechanism connected hydraulically or mechanically to two movable cone plates placed on the opposite side. CONSTITUTION:A fixed cone plate 20 formed in one unit with an input shaft is to form a cylinder wall 21 on a movable cone plate 21 together with the partition wall 23 fixed on an input shaft to partition an oil pressure chamber 23a, and valves 26, 40 and a pressure oil supply pipe 62 are to be fixed in hollow portion 69. A pulley K on the driven side is to be composed of a fixed cone plate 50 and a movable cone plate 51,and pressure oil chamber 53a, a pressure oil supply pipe 64 and controlling valves 56, 45 are to be provided thereto. A servo mechanism P is also to be provided to obtain the displacement quantity responsing to a speed change signal, and connection members 42, 47 connecting the servo mechanism P and controlling valves 40, 45 are to be secured. The variation performance of the radius of the belt winding surface can consequently be carried out satisfactorily with a little control signal energy and a simple structure.

Description

Detailed Description of the Invention (Industrial Field of Application) The present invention relates to a continuously variable belt transmission mounted on a vehicle, etc., and in particular to a V-belt wound around a drive pulley on an input shaft and a driven pulley on an output shaft. The present invention relates to a gear ratio control method and apparatus for a continuously variable belt transmission having a configuration for steplessly controlling the gear ratio of an input/output shaft by controlling the rotation radius of the belt winding surfaces of the driving and driven pulleys.

(Prior art and problems) In such a continuously variable belt transmission, in order to effectively transmit torque, it is necessary to apply tension to the belt according to the transmitted torque, such as by applying lateral pressure to the belt using fluid pressure. Even when controlling the radius of the belt winding surface in order to change the belt tension, it is necessary to maintain the belt tension.

JP-A-55-65755, JP-A-60-1254
Publication No. 50 states that the oil pressure from the pump is regulated using the rotation speed of the drive pulley and the gear ratio as factors, and the oil pressure is controlled by the rotation speed of the drive pulley (engine rotation speed) and the throttle opening through a slide valve. By supplying the movable conical plate that makes up the drive pulley to a hydraulic cylinder that slides in the axial direction, the regulated hydraulic pressure is used to control the radius of the belt winding surface of the drive pulley while maintaining the side pressure of the belt. Disclosed.

In this 413 construction, the effective area of the hydraulic cylinder of the movable conical plate of the driven pulley is set smaller than that of the driving pulley, and when sliding the gear ratio toward the high speed side, the diameter of the driving pulley changes. The resulting belt tension causes the movable conical plate of the driven pulley to slide against the lateral pressure, thereby controlling the radius of the belt winding surface of the driven pulley. Therefore, an unnecessary load is applied to the belt, which has an unfavorable effect on the durability of the belt. In addition, when sliding the gear ratio to a lower speed side, the lateral pressure on the driving pulley is released by draining oil from the hydraulic cylinder, and the lateral pressure on the driven pulley is used to control the belt winding surface radius in the same way. The lateral pressure may be lower than necessary.

On the other hand, U.S. Patent No. 3,600,961 discloses that high-pressure oil at a constant pressure and low-pressure oil whose pressure is regulated by the gear ratio, etc. are obtained, and the side pressure of the driving pulley and driven pulley is achieved by the low-pressure oil, and the high-pressure oil is used during gear shifting. A structure is disclosed in which control is performed by supplying the belt to a hydraulic cylinder of a pulley with a large concave radius.

However, even in this structure, it is necessary to use a side pressure higher than the required side pressure depending on the speed change region, and there are disadvantages such as a large pressure loss.

(Object of the Invention) In order to solve the problems of the prior art described above, the present invention provides a belt continuously variable transmission system that supplies pressure fluid corresponding to the transmitted torque to a driving pulley and a driven pulley, and enables speed change while maintaining belt tension. The purpose is to provide a control method and a control device for the machine.

(Structure and operation of the invention) In order to achieve the above object, in the present invention, a belt is wound between a driving pulley on an input shaft and a driven pulley on an output shaft, and a transmission is provided to maintain the tension of the belt. A belt that supplies pressure oil corresponding to the torque to a hydraulic cylinder provided on a movable conical plate of both pulleys, causes the movable conical plate to slide, and expands or contracts the radius of the belt winding surface of the pulley to change speed. In the continuously variable transmission, the speed change signal generation mechanism is configured as a servo mechanism that outputs an amount of movement equal to the sliding motion of the movable conical plates of both pulleys corresponding to the speed change ratio. That is, a pilot valve that slides in response to a hydraulic signal corresponding to a vehicle running parameter or an engine parameter, and one of a piston and a cylinder defining a hydraulic chamber are made slidable, and the slidable piston or cylinder is provided with a hydraulic chamber. By providing a communication port and connecting the communication port to the oil drain port or pressure oil supply port carved into the pilot valve, a piston or cylinder that can slide in the same direction and amount as the pilot valve can be created. It is constructed into a so-called tracing mechanism that can slide.

Furthermore, by hydraulically or mechanically connecting the movable conical plates of both pulleys to the sliding member of the speed change signal generating mechanism and making them slide together, the sliding amount of the pulleys is equal to the total movement of the speed change signal generating mechanism. It is applied to the movable conical plate to control the radius of the belt winding surface.

Furthermore, in the present invention, the servo mechanism, which is the speed change signal generation mechanism, and the movable conical plate of the pulley are configured to slide together, and the shift valve, which is connected to the speed change signal generation mechanism and slides together, corresponds to the transmitted torque. A supply port for supplying pressure oil;
An oil drain port is provided, and the pressure oil supply port or the oil drain port is selectively connected to the communication port of a sliding valve that slides integrally with the movable conical plate and constantly communicates with the hydraulic cylinder of the movable conical plate. By connecting the slide valve to the movable conical plate, the slide valve and the movable conical plate are configured to slide together as a parallel structure.

(Embodiment of the present invention) A preferred embodiment of the present invention will be specifically described below based on the drawings.

FIG. 1 is a schematic diagram showing a power transmission path when a continuously variable belt transmission according to the present invention is mounted on a vehicle, and FIG. 2 shows its detailed structure.

In Figure 1, the output torque of engine A is output φ + h
Power is supplied from B to a belt continuously variable transmission via a well-known torque converter C via a torque converter output shaft. Input gear E meshes with gear F, which is connected to and disconnected from input shaft G by a forward clutch. When the clutch is engaged, torque is transmitted to drive pulley H, and output M J is generated by belt ■.
The torque of the output shaft J, which is applied to the upper driven pulley K, acts as a deceleration mechanism and drives the wheels via the differential mechanism M.

On the other hand, the human gear E is meshed with the reverse gear which is connected to and disconnected from the output shaft J by the reverse clutch N via the idle gear.When traveling backward, the wheels are rotated by releasing the forward clutch and connecting the reverse clutch N. Go backwards.

In FIG. 2, an engine output shaft B (portions corresponding to those in FIG. 1 are indicated by the same reference numerals) is coupled to a dollar converter cover 1, and rotates integrally with a support member 2 of a pump impeller 3 coupled to the cover 1. do. The turbine impeller 4 is integrally connected to the dollar converter output shaft, and the transmitted torque is inputted to the transmission by the transmission's human gear E rotating together with the output shaft. 6 is a known lock-up clutch, and 5 is a stator which is supported by a shaft via a one-way clutch 8. A cover 11 of a torque detection mechanism 10 for obtaining a transmission torque signal for regulating line pressure is fitted into the recess 9 at the rear end of the dollar converter output shaft via a bearing.

The manual gear E is always in mesh with a gear F rotatably supported on the input shaft G of the continuously variable belt transmission, and the rotation of the gear F is transmitted to the input request G by the forward clutch 12.

The forward clutch 12 is a well-known multi-disc clutch, and has a hydraulic chamber 12f defined by a piston 12b in a clutch housing 12a fixed to an input shaft G.
With the pressure oil supplied by to communicate. 12c is a clutch spring.

A drive pulley H is provided on the input shaft G so as to rotate together therewith. The drive pulley H is composed of a fixed conical plate 20 formed integrally with the input shaft G and a movable conical plate 21 supported on the shaft so as to be slidable in the axial direction. An endless belt I is wound between driven pulleys having the same structure as those on FIIIJ.

The movable conical plate 21 has a cylinder wall 21a that forms a hydraulic chamber 23a together with a partition wall 23 fixed on the input shaft G, and the partition wall 23 has an oil passage 24 for supplying and discharging pressure oil to the hydraulic chamber 23a.
will be established. 22 is a cylinder cover. A valve 26, 40 and a pressure oil supply pipe 62 for controlling the supply and discharge of pressure oil to the hydraulic chamber 23a are fitted into the hollow portion 29 formed in the input shaft G. 28 is a ball bearing for smooth sliding of the movable conical plate 21.

The output 11ilhJ has a small diameter gear 1 that constitutes a reduction mechanism.
5 is fixed, and the small diameter gear 15 and the large diameter gear 16 are connected at 0V and transmitted to the differential mechanism M.

A reverse gear N rotatably supported on an output shaft J meshes with a human gear E via an idle gear (not shown), and transmission of its rotation to the output shaft J is disconnected by a reverse clutch 13.

The reverse clutch 13 is a well-known multi-disc clutch having the same configuration as the forward clutch 12, and includes a tarlatch housing 13a, a piston 13b, a clutch spring 13C5, and a hydraulic chamber 13f.
Pressure oil is supplied to the hydraulic chamber 13f through an oil passage 13d provided in the output shaft J and a boat 1 in the clutch housing 13a.
3e.

A driven pulley K is further provided on the output shaft J so as to rotate together with the output shaft J. The driven pulley is composed of a fixed conical plate 50 and a movable conical plate 51, and the movable conical plate 51 is connected to the cylinder 1.
51a, and the cylinder wall 51a defines a hydraulic chamber 53a together with a partition wall 53 fixed on the output shaft.

Several springs 60 are installed between the partition wall 53 and the movable conical plate 51.
Attach. 58 is a ball bearing for smooth sliding of the movable conical plate 51, and 52 is a cylinder cover.

The hollow portion 59 extends over the sliding area of the movable conical plate 51 of the output shaft J.
A pressure oil supply pipe 64 and a control valve 5 are installed in the hollow part.
6.45 is inserted. Pressure oil from the control valves 45 and 56 is supplied to the hydraulic chamber 53a through an oil passage 54 provided in the boat 55 and the partition wall 53.

Next, m! in response to the gear shift signal! The structure for controlling the radius of the belt winding surface of the riIJ pulley H1 movable pulley will be explained with reference to FIGS. 2 and 3.

P is a servo mechanism for obtaining a displacement amount corresponding to a shift signal, and includes a pilot valve 37, a servo piston 36 fixed to the transmission case, and together with the piston, a hydraulic chamber 36c is defined, It consists of a servo cylinder 35 that slides in the axial direction on a fixed piston,
A connecting member 42 for moving the control valve 40 of the drive pulley H is fixed to the servo cylinder 35 by a bolt 44, and a connecting member 47 for moving the control valve 45 to the driven pulley is fixed by a bolt 49. That is, the control valve 40
．． 45 is configured to move together with the servo cylinder of the servo mechanism P.

Reference numeral 41.46 indicates a fixed portion of the connecting member 42.47 on the control valve side.

The structure of the control valve fitted into the hollow portion 29.59 of the input shaft G1 and the output shaft J will be explained.

The control valve has a pin 27 sliding with a movable conical plate 21.51.
．． 57, and a second slide valve 40.45 inserted inside the slide valve and sliding integrally with the servo cylinder 35. The first slide valve 26.56 is the hydraulic chamber 2 of the movable conical plate 21.51.
Oil grooves 26a, 56a always communicating with the pressure oil boats 25° 55 of 3a, 53a, and communicating with the oil grooves 26a, 56a,
It has boats 26b, 56b bored on the inner surface. Second
The slide valves 40.45 have oil grooves 40d and 45d, each of which is supplied with line pressure oil from a line pressure oil passage 61 via a boat 63.65 via a pressure oil supply pipe 62.64, and the oil groove 40d.

45d, and supply side oil grooves 40a, 45a that communicate with the boats 26b, 56b of the first slide valve 26.56 by sliding and supply line pressure oil. Bow of the first slide valve 26.56)-26b.

56b, the hydraulic chamber 23a of the movable conical plate 21.51
, 53a to the oil drain passages 43, 48, respectively, and oil drain side oil grooves 40b, 45b and oil drain boats 40e, 45e.

FIG. 4 shows a hydraulic circuit for controlling the gear ratio of the continuously variable belt transmission of the present invention.

When the manual valve T is operated and slid to the illustrated position, the line pressure oil sent from the oil reservoir 101 by the pump 100 is regulated by the pressure regulating valve Q, and reaches the forward clutch 12 via the manual valve T through the oil passage 105. The clutch transmits the output torque of the torque converter C to the input shaft G, so that the drive pulley H rotates.

The pressure regulating valve Q regulates the oil pressure so as to obtain the optimum belt side pressure according to the torque transmitted by the continuously variable belt transmission. A lever 126 that responds to the gear ratio is brought into contact with a protrusion 123 that biases the slide valve 121 to the left via a spring 124 at one end of the valve 121, and a lever 128 that responds to input shaft torque is brought into contact with the protrusion 122. The slide valve 121 is configured to be brought into contact with the slide valve 121 via the spring 125. This adjusts the oil pressure to be proportional to the input shaft torque and gear ratio.

As shown in detail in FIG. 5, a torque detector 4 or 10 applies a displacement to the lever 128 that is proportional to the torque.

The torque detection mechanism supports an input gear E at the end of the output axis of the torque converter so as to be easily slidable in the axial direction by means of a ball bearing 14, etc., and the human power gear E is configured as a helical gear.

In response to the torque of the input gear E, the thrust force causes the gear E to move 8 times in the axial direction.
5', and is transmitted to lever 128 by pin 129. 11
is the cover.

The gear ratio responsive lever 126 is connected to the servo cylinder 35 of the servo mechanism P by a rod 127.

The pressure regulating valve structure in the present invention is not limited to that shown in the embodiments. Any device that can obtain hydraulic pressure corresponding to the transmission torque of the continuously variable belt transmission may be used.

For example, a torque signal may be obtained as an electric signal using a known torque sensor or the like, and the pressure may be regulated using a 7M or 6n valve, or the pressure may be regulated using an engine rotation speed signal and a gear ratio signal as in the above-mentioned known example.

The regulated line pressure oil is sent to the supply pipe 64 of the driven pulley through the oil passages 10B and 107 and to the supply pipe 62 of the driving pulley through the oil passage 108 at the same time as the forward clutch is actuated. On the other hand, the line pressure oil from the branch passage 109 is supplied to the oil passage 1.
10 leads to the pressure oil boat 36a of the servo mechanism P, and is also supplied to the governor valve R through the oil path 111. Governor valve R
is a well-known centrifugal force hydraulic control valve used in automatic transmissions, etc., and is driven by an output shaft to obtain governor pressure oil proportional to vehicle speed. The governor pressure oil is introduced into the oil chamber 38 formed at the end of the pilot valve 37 of the servo machine #FfP through the oil passage 112 via the boat 39, and is used as a vehicle speed signal for speed change control.

Further, the governor pressure oil is supplied as a signal pressure to a valve S that controls a lock-up clutch of a torque converter through a branch path 113.

One oil passage 114 from the pressure regulating valve Q supplies line pressure oil to the torque converter through a branch passage 116, and is further introduced into the hydraulic chamber of the lock-up clutch via an oil passage 115 by a control valve S. The oil passage 117 is a return oil passage of the torque converter, 102 is a check valve, and 103 is a cooler.

As described above, the pilot valve 37 of the servo mechanism P has the hydraulic chamber at one end supplied with the vehicle speed signal pressure, that is, the governor pressure, but the other end is negatively biased by the lever 33 with a force proportional to the throttle opening of the engine. .

The throttle opening detection mechanism U is fitted into a support member 30 attached to the transmission case.

As shown in FIG. 6, the throttle opening detection mechanism U includes a cylindrical member 130 and sliding members 131 and 132 inserted into both ends of the cylindrical member 130 so as to be slidable in the axial direction. Consists of 133.

When a lever 134 connected via a link to a rod 135 that is linked to an accelerator pedal or an engine throttle applies a displacement proportional to the throttle opening to the sliding member 131, the sliding member 132 is displaced via a spring, The lever 31 is rotated, and the lever 334C that contacts the pilot valve 37 is transmitted by the link 136. Note that the relationship between the spring load and the amount of displacement of the spring 133 must be determined based on the relationship between the throttle opening degree and the speed change characteristics, and it is necessary to configure the spring 133 with an appropriate spring rate using coil springs with unequal pitches, etc. be.

In addition, the lever 33 can be directly connected to the pyront valve 3 of the servo mechanism P.
7, the displacement amount of the throttle opening detection mechanism U is also influenced by the 8 movement of the pilot valve 37, and the servo valve 37 is controlled by the vehicle speed signal, throttle opening signal, and gear ratio signal. .

In FIG. 3, the forward clutch is actuated by operating the manual lever, torque is transmitted to the drive pulley H1 ratio drive pulley K and output shaft J, the vehicle starts, and when the vehicle speed increases, the hydraulic chamber 38 of the pilot valve 37 opens. The governor pressure increases and the pilot valve 37 is slid to the right, and the pressure oil supply groove 37a of the pilot valve 37 and the oil passage 35c of the servo cylinder are connected, and the line pressure oil supplied to the boat 36a is connected to the fixed piston 36. Oil passage 36b and servo cylinder 35 drilled in
The oil is supplied to the oil pressure chamber 36c through oil passages 35a and 35b drilled in the oil pressure chamber 36c, and moves the servo cylinder 35 to the right.

When the vehicle speed increases and the pilot valve 37 continues to move eight times to the right, only the pilot valve 37 is moved by the servo cylinder 35.
continues to move to the right. In other words, it is a tracing mechanism.

When the throttle opening is increased by depressing the accelerator pedal relative to the vehicle speed, the pilot valve 3 is activated by the lever 33.
7 moves to the left, the oil drain groove 37'b communicating with the oil drain boat 37c connects with the boat 35e of the servo cylinder 35, and the connection between the pressure oil supply groove 37a and the oil path 35c of the servo cylinder is cut off. Therefore, the pressure oil in the hydraulic chamber 36c is discharged through the oil passage 35d, and the servo cylinder 35 is also moved to the left.

The movement of the servo cylinder 35 is caused by connecting the drive pulley H1 to the second slide valve 40.47 to the driven pulley by a connecting member 42.47.
45 is moved.

The state of the illustrated continuously variable transmission is such that the drive pulley H has the minimum belt winding surface radius, the driven pulley has the maximum radius, and the gear ratio is maximum (LOW).

As the vehicle speed increases, the second slide valve 40 on the driving side moves upward due to the movement of the servo cylinder 35, and the pressure oil supply groove 40
a communicates with the boat 26b of the first slide valve 26, and line pressure oil is supplied to the hydraulic chamber 23a.

Subsequently, the oil drain groove 45b communicating with the oil drain path 48 of the second slide valve 45 on the driven side is connected to the boat 5 of the first slide valve 56.
6b, the pressure oil in the hydraulic chamber 53a is discharged, and the movable conical plate 2.1.51 begins to slide together.

Since the first slide valve 25.5'6 slides together with the movable conical plate, the above-mentioned boat communication relationship is such that the second slide valve does not continue to open and when the servo cylinder 37 stops moving due to the signal. By sliding the first slide valve 26.56, the above-mentioned communication relationship is severed and the movable conical plate stops. By sliding the movable conical plate 21.degree. 51, the winding radius of the belt on the driving side is increased and that on the driven side is controlled to be small, and the speed is changed to a high speed gear with a small gear ratio.

Due to the movement of the pilot valve 37 of the servo mechanism P, the spring 13 of the throttle opening detection mechanism U is activated via the L/bar 33.
3 is compressed. When the throttle opening is increased from the minimum gear ratio (HIGH) state, the pilot valve 37 moves to the left, and the second slide valve 40 moves integrally with the servo cylinder 35.
．． 45 also moves, and first, the pressure oil supply groove 45a of the second slide valve 45 on the driven side connects with the boat 56b, and the hydraulic chamber 53 is connected to the boat 56b.
Line pressure oil is supplied to a, and then the drain oil 11 of the second slide valve 40 on the driving side communicates with the boat 26b, and the pressure oil of the hydraulic pressure) E 23 a is discharged, and the pressure oil of the second slide valve 40 on the drive side is connected to the boat 26b, and the pressure oil of the two movable conical plates 2
1.51 begins to slide in the direction of the gear change hole size.

The first slide valve 40.45 moves together, the slide valve 40.45 and the second slide valve 40.45 move together, and the slide valve 40.45 and the movable conical plate 21.51 move together by a following mechanism. Because it has a structure that moves in one piece, even if pressure oil is supplied to the hydraulic chamber of the boob, which slides in the direction where the belt winding surface radius is large, the movable conical plate does not slide, and the belt winding surface radius increases. Both movable conical plates begin to slide only when the hydraulic chamber of the pulley that slides to the small side is connected to the oil drain path, that is, when both oil drain and oil supply conditions are satisfied. Therefore, the second slide valve 40.
By connecting the arrangement of 45 supply grooves and oil drain grooves from the supply side, and then connecting the oil drain side to start sliding the movable conical plate, it is possible to change speed while maintaining belt tension as much as possible. becomes possible. Furthermore, it is more effective to provide a restriction in the oil drain path and make it smaller in cross-sectional area than the oil supply path.

FIG. 7 schematically shows the positional relationship between the hydraulic chamber boat on the driving side and the driven side, the supply groove of the second slide valve, and the oil drain groove.

In the figure, a is a driving side hydraulic chamber boat, b is a driven side hydraulic chamber boat, and Sl.

El are the supply groove, oil drain groove, and S2 of the second slide valve on the driving side, respectively. E2 is a supply groove and an oil drain groove of the second slide valve on the driven side.

Figures 1 to 3 show the progress of sliding toward the high-speed stage side.
The second slide valve moves to the right in the figure.

In Figure 1, first, the drive side hydraulic chamber boat a is connected to the pressure oil supply groove S.
1 and the supply of line pressure oil is started. However, the oil in the driven side hydraulic chamber has not yet been drained and the movable conical plate cannot slide. When the second slide valve further moves to the right and reaches the position shown in Fig. 2, the driven side hydraulic chamber boat b starts communicating with E2, and the sliding of the movable conical plate corresponds to the amount of oil drained as shown in Fig. 3. will be held.

When the second slide valve is stopped at this position, the communication between the driven side hydraulic chamber boat b and E2 is cut off due to the rightward movement of the first slide valve, which slides integrally with the movable conical plate, as shown in Fig. 4.
The movable conical plate stops.

The drive-side hydraulic chamber boat a may continue to communicate with Sl.

Next, when the second slide valve is shifted to the left, i.e., the gear ratio is shifted toward a higher gear ratio, as shown in Fig. 5, the communication between the driving side hydraulic chamber boat a and 31 continues to be cut off, and the driven side hydraulic chamber boat b becomes connected to S2. Although the line pressure is supplied by connecting, the hydraulic chamber boat a is
The movable conical plate will not slide to the left until the drive-side hydraulic chamber is drained.

Note that the present invention is not limited to the O-11 structure shown in the embodiment, and instead of the servo mechanism of the embodiment, an i
The slide valve may be driven by a motor that responds to a speed change command, and the movable conical plates of the driving pulley and driven pulley are connected to each other so that they slide together, and the line pressure is supplied to and discharged from the hydraulic chamber. is carried out using an electric TN valve, and the system is configured to first supply oil to a pulley whose belt winding surface radius is expanded based on a speed change signal, and then drain oil from the hydraulic chamber of a pulley whose belt winding surface radius is reduced. The same effect can be obtained even if

(Effects of the Invention) As explained above, in the present invention, the movable circular IIT plates of the drive pulley and driven pulley of the belt continuously variable transmission are slid together by the servo mechanism that outputs the speed change signal, so the belt is not required. It is possible to expand or reduce the radius of the belt winding surface of the pulley while always maintaining the side pressure corresponding to the transmitted torque without applying any heavy load.
Since the servo wt has a tracing structure, it is possible to obtain an output of the amount wJ, which is equal to the sliding amount of the movable conical plate, with a simple structure, and a relatively small signal pressure or a small energy signal can be used to generate an output with a large actuation force. can be obtained.

It should be noted that the present invention is not limited to the structure shown in the embodiment, and the hydraulic oil of the servo mechanism is high pressure oil different from the pressure oil for pulley side pressure, and the sliding body of the servo mechanism is used to mechanically move the movable conical plate of the boot. Alternatively, the pilot valve may be driven by a sliding valve driven by an electric signal such as a linear solenoid instead of being driven by a hydraulic signal.

[Brief explanation of drawings]

1 to 6 show a belt continuously variable transmission according to an embodiment of the present invention, in which FIG. 1 is a schematic diagram of the power transmission system, and FIG.
The figure is a sectional view of the mechanism, Figure 3 is an enlarged sectional view of the main parts of the mechanism, and Figure 4 is a sectional view of the mechanism.
The figure is a hydraulic circuit diagram, and FIGS. 5 and 6 are partially enlarged sectional views. A... Engine H... Drive pulley ゛ ■... Belt K... Driven pulley 20.50... Fixed conical plate 21.51... Movable conical plate 23a, 53a... Hydraulic chamber 26.40, 45.56...Slide valve patent issued,
Patent attorney representing Honda Motor Co., Ltd.
1) Part 1 Patent Attorney University
Kuni Hashi Patent Attorney Koyama
Patent Attorney No. 1) Mote Motouri Neyama JE & (Voluntary) May 11, 1988 41F, J'l Agency Director Akio Kuroda Patent application filed on April 30, 1986 (4) 2 ) Name of the invention Belt continuously variable transmission 3, Relationship with the person making the amendment 211 cases Patent applicant (53.2) Honda Motor Co., Ltd. 4, Agent 5, Date of amendment order Voluntary 6, Subject of amendment Details Column 7 for detailed explanation of the invention
, content of correction

Claims (4)

[Claims] (1) Pulleys consisting of a fixed conical plate and a movable conical plate are provided on the input and output shafts, the belt is wound between them, and the movable conical plate is slid on the shaft to expand or reduce the radius of the belt winding surface. In a belt continuously variable transmission that at least controls the gear ratio, two movable conical plates are arranged on the same side, and the movable conical plates are slid by a servo mechanism hydraulically or mechanically connected to the two movable conical plates. A belt continuously variable transmission characterized by controlling. (2) In the belt continuously variable transmission according to claim 1, the servo mechanism that controls the sliding of the movable conical plate of the pulley has one fixed piston and the other sliding piston that defines the hydraulic chamber. A cylinder, a piston and a pilot valve that are slidably inserted into a hollow part having the same axis as the cylinder, and a supply port and a hydraulic chamber that constantly communicate with a hydraulic oil source in the sliding member of the piston or cylinder. An oil drain port is provided that communicates at all times, and the pilot valve has a supply groove that connects with the supply port of the sliding member and supplies hydraulic oil to the hydraulic chamber, and a supply groove that connects with the oil drain port and communicates the hydraulic chamber with the oil drain path. A continuously variable belt transmission characterized by having a servo mechanism and having an oil drainage groove. (3) In the belt continuously variable transmission servo mechanism according to claim 2, the piston is fixed to the transmission case,
A servo mechanism is provided on the outer periphery of the piston, in which a cylinder, which together defines a hydraulic chamber, is slidable in the axial direction, a pilot valve is fitted therein, and a connecting member for sliding a movable conical plate of a pulley is fixed to the cylinder. Continuously variable belt transmission. (4) In the belt continuously variable transmission according to claim 2, an oil chamber is provided at one end of the pilot valve that is inserted into the hollow part of the piston and the cylinder on the same axis, and signal pressure oil is introduced; A continuously variable belt transmission characterized by comprising a servo mechanism that presses the other end with a convex element that moves in accordance with vehicle or engine parameters.