JPH0563663B2 - - Google Patents

Description

[Detailed description of the invention]

TECHNICAL FIELD The present invention relates to a spool valve type shift speed control valve device used in a hydraulic system for a belt-type continuously variable transmission, and in particular, when the shift speed control valve device is duty-controlled by increasing the responsiveness of switching operation. The present invention relates to a technology that widens the range in which flow rate can be controlled with respect to changes in duty. PRIOR ART A pair of variable pulleys whose effective diameters are changed by moving mutually opposing rotating bodies provided on a rotating shaft toward and away from each other by a hydraulic cylinder, and a variable pulley that is wound between the variable pulleys. In a belt-type continuously variable transmission equipped with a transmission belt, by supplying hydraulic oil to a hydraulic cylinder that changes the effective diameter of one of the variable pulleys, or allowing discharge of hydraulic oil discharged from the hydraulic cylinder. There is a hydraulic device that changes the gear ratio of a belt-type continuously variable transmission. If such a device is used in a car, the engine rotation speed can be controlled to the optimum rotation speed by continuously changing the gear ratio according to the driving condition, so that a suitable fuel efficiency rate can be obtained. be.
Such a device includes a valve body in which a cylinder bore is formed, a spool shaft and a plurality of spool lands formed in a large diameter part in the axial direction, and the valve body is slidably fitted into the cylinder bore. the spool valve; and a valve driving device that applies a predetermined hydraulic pressure to the end face of the spool valve to selectively position the spool valve in two positions in the axial direction; The spool land portion is inserted into a supply passage through which hydraulic oil is supplied to the hydraulic cylinder and a discharge passage through which hydraulic oil is discharged from the hydraulic cylinder, and as the spool valve element moves between the two positions. By opening and closing a predetermined port opened in the cylinder bore, the flow of hydraulic oil in the supply passage and the discharge passage can be switched between a state where it is allowed and a state where it is suppressed, thereby changing the gear ratio change speed ( A shift speed control valve device may be used to adjust the shift speed). However, in such a shift speed control valve device, two positions of the spool valve are generally determined so that the spool land completely opens and closes the predetermined port, and the movement stroke of the spool valve is limited. It was set relatively large. For this reason, the responsiveness of the switching operation of the shift speed control valve device is not necessarily sufficient, and when the shift speed control valve device is duty-controlled, the range in which flow can be controlled in response to duty changes is relatively narrow, and high-precision It was difficult to control the speed of change in gear ratio. Purpose of the Invention The present invention has been made against the background of the above-mentioned circumstances, and its object is to provide a belt type that has high speed change responsiveness in switching operation and can obtain sufficient speed change speed in rapid speed change. An object of the present invention is to provide a hydraulic system for a continuously variable transmission. Structure of the Invention The gist of the present invention to achieve the above object is to supply hydraulic oil to a hydraulic cylinder for changing the effective diameter of a variable pulley or to allow discharge of hydraulic oil from within the hydraulic cylinder. In a belt-type continuously variable transmission that changes the gear ratio by a shift switching valve device driven to two positions, and interposed between the shift switching valve device and the hydraulic cylinder,
A hydraulic system equipped with a shift speed control valve device that is driven to two positions: a state where the flow of hydraulic oil supplied to the hydraulic cylinder or a hydraulic oil discharged from the hydraulic cylinder is permitted and a state where the flow is suppressed. The shift speed control valve device includes: (a) an upstream supply port to which hydraulic fluid is exclusively supplied from the shift switching valve device, and a supply port that exclusively sends hydraulic fluid in the hydraulic cylinder to the shift switching valve device; a downstream supply port for supplying the hydraulic oil supplied to the upstream supply port passage to the hydraulic cylinder; (b) a supply spool land section that opens and closes between the upstream supply port and the downstream supply port; A discharge side spool land section that opens and closes between the side discharge port and the downstream side discharge port is provided, and the supply side spool land section and the discharge side spool land section are located in two positions: a flow-permitting side position and a flow-restricting side position. (c) the supply side spool land portion has a spool valve actuated between the upstream supply port and the downstream supply port; The flow rate of hydraulic oil from the upstream supply port to the downstream supply port is suppressed, and when the supply spool land opens between the upstream supply port and the downstream supply port, the upstream supply is suppressed. A throttle passage is provided for guiding hydraulic fluid from the port to the upstream discharge port, and (d) at least the flow-permitting side position of the two positions of the spool valve is connected to the supply-side spool land of the spool valve. In order to allow the flow of hydraulic oil, the openings of the spool land and the discharge spool land are positioned to partially open. Operation and Effects of the Invention With this arrangement, at least the position on the flow-permitting side of the positioning position of the spool valve is determined so as to partially open the opening formed by the spool land, so that the movement stroke of the spool valve can be reduced. The response time in the switching operation of the shift speed control valve device is improved, and when controlling the duty of the shift speed control valve device, the range in which the flow rate can be controlled for the duty ratio is expanded, and the speed of change of the gear ratio is achieved with high precision. Control becomes possible. Moreover, even if the opening is partially opened by the spool land in the flow-permitting state of the shift speed control valve device, the flow is passed through the throttle passage provided in the supply side spool land and the upstream discharge port to the hydraulic cylinder. Since the hydraulic oil is supplied, the flow rate during the rapid speed change is ensured, and a sufficient speed change can be obtained. Embodiment Hereinafter, an embodiment of the present invention will be described in detail based on the drawings. In FIG. 1, 10 is a belt-type continuously variable transmission (hereinafter referred to as CVT) which is connected to an automobile engine (not shown) and changes its rotation at a predetermined gear ratio and transmits it to wheels, etc. A hydraulic device 12 for changing (shifting) the gear ratio is provided. On the other hand, the gear ratio controller 14 has
Throttle signal ST representing the engine throttle operation amount from the throttle sensor 16, primary variable pulley rotation sensor 18, secondary variable pulley rotation sensor 20, transaxle oil temperature sensor 22, etc.
A rotation signal RI representing the rotation speed of the primary variable pulley 24 (engine rotation speed) of the CTV 10, a rotation signal representing the rotation speed of the secondary variable pulley 26
RO, temperature signal indicating transaxle oil temperature
TH etc. are supplied respectively. The gear ratio controller 14 grasps the operating state based on these signals, determines the optimum target gear ratio or target engine rotation speed to obtain the desired operating state, for example, mainly the minimum fuel efficiency rate, A drive signal is sent to the solenoid valves 28 and 30 in the hydraulic system 12 so that the gear ratio or engine rotation speed matches the target gear ratio or target engine rotation speed.
Supply SD1 and SD2 respectively. The CVT 10 and hydraulic system 12 are configured as shown in FIG. 2. That is, the CVT 10 has a primary rotation shaft 32 and a secondary rotation shaft 3.
A pair of primary side variable pulley 24 and secondary side variable pulley 26 provided in 4, and those variable pulleys 2
A transmission belt 36 is provided which is wound between the engine and the primary rotating shaft 32.
The rotational force transmitted to is transmitted to the secondary rotation shaft 34 via the transmission belt 36, and is further connected to wheels etc. via a differential device (not shown) via a gear device 38 that can change the direction of rotation. The signal is transmitted to the output shaft 40. Primary side variable pulley 24
is a fixed rotating body 4 fixed to the primary rotating shaft 32
2, and a movable rotating body 46 that is fitted onto the primary rotating shaft 32 in an axially movable but non-rotatable manner and is moved in the axial direction by the primary hydraulic cylinder 44. The groove width of the V-groove formed between the fixed rotating body 42 and the movable rotating body 46, that is, the effective diameter of the primary variable pulley 24 (the diameter of the transmission belt 36) is changed according to the oil pressure. ing. Secondary variable pulley 26
Similarly, a fixed rotating body 48 is fixed to the secondary rotating shaft 34, and a secondary hydraulic cylinder 5 is fitted to the secondary rotating shaft 34 so as to be movable in the axial direction but not rotatable.
A movable rotating body 5 axially moved by
2, and the effective diameter is changed by changing the groove width of the V groove formed between the fixed rotary body 48 and the movable rotary body 52 according to the hydraulic pressure of the secondary side hydraulic cylinder 50. It is becoming more and more common.
Note that the primary side hydraulic cylinder 44 has a double piston structure, so that even if the same line hydraulic pressure is supplied, a larger output than the secondary side hydraulic cylinder 50 can be obtained. The hydraulic system 12 includes a hydraulic system that generates hydraulic oil (line hydraulic pressure) at a predetermined pressure corresponding to a hydraulic signal representing the gear ratio supplied from the sensing valve 54 and a hydraulic signal representing the throttle opening supplied from the throttle valve 66. By supplying line hydraulic pressure to the generator 56 and the primary hydraulic cylinder 44 to increase the pressure, or by allowing discharge of hydraulic oil from the primary hydraulic cylinder 44 and decreasing the pressure,
A shift switching valve device 58 that switches the shift direction (speed ratio change direction) and a shift speed ( A shift speed control valve device 60 for changing the speed ratio change speed) is provided. Note that the secondary hydraulic cylinder 50 and the sensing valve 54
is designed to be constantly supplied with line hydraulic pressure. To further explain the hydraulic system 12 based on FIG. 3, the hydraulic pressure generator 56 includes a pump device 62,
Consisting of a regulator valve 64, a throttle valve 66, a cooler 68, a cooler pressure valve 70, etc., the line oil pressure, which changes depending on the throttle opening and gear ratio, is transferred via an oil passage 72 to a shift switching valve device 58, a shift speed control valve The liquid is supplied to the device 60, the sensing valve 54, and the like. The sensing valve 54 includes a spool valve 74 and a movable rotating body 46 of the primary variable pulley 24.
A sensing piston 76 is provided which moves together with the sensing piston 76 to apply a biasing force corresponding to the gear ratio of the belt type continuously variable transmission 10 to the spool valve element 74 via a spring, and an input port 78 communicating with the line oil passage 72. By changing the communication area between the output port 80 and the spool valve 74 responsive to the gear ratio, the gear ratio pressure signal corresponding to the gear ratio shown in FIG.
4 input port 82. The throttle valve 66 includes a spool valve 84,
A piston 90 is provided, which engages with a cam 86 that rotates with the throttle operation and is moved with the throttle opening, thereby applying a biasing force corresponding to the throttle opening to the spool valve element 84 via a spring 88. By adjusting the flow area of the input port 92 communicating with the line oil passage 72, the throttle pressure signal representing the throttle opening shown in FIG. 5 is transmitted from the output port 94 to the input port 96 of the regulator valve 64. Supplied. The regulator valve 64 has a spool valve 98.
and a valve plunger 100 that receives the gear ratio pressure signal and the throttle pressure signal to control the spool valve element 98. By adjusting the area, the line oil pressure of the line oil passage 72 communicating with the line port 102 is adjusted as shown in FIG. In other words, since the hydraulic pressure output from the pump device 62 is generated by the pump 106 driven by the engine, the hydraulic pressure must be at the minimum necessary level to prevent slippage in the transmission belt 36 of the CVT 10 so as not to increase power loss. This pressure is applied to reduce the fuel efficiency of the vehicle. In addition,
The pump device 62 uses the pump 106 to return hydraulic oil from the cooler 68, sensing valve 54, throttle valve 66, shift switching valve device 58, shift speed control valve device 60, etc. to the tank 108 through a drain pipe (not shown). Pumping, relief valve 11
The oil is supplied to the regulator valve 64 through an oil passage 112 to which a 0 is attached. The shift switching valve device 58 and the shift speed control valve device 60 are provided with electromagnetic valves 28 and 30 and spool valves 118 and 120, respectively. Line oil pressure is supplied to the electromagnetic valves 28 and 30 via line oil passages 72, respectively. The solenoid valve 28 is equipped with an orifice 122 in a passage communicating with the oil passage 72.
When the line hydraulic pressure passing through the orifice 122 is applied to the end face of the spool valve element 124 of the spool valve 118 by the closing operation (when not energized) of the solenoid valve 28, the line pressure is applied to the end face of the spool valve element 124 of the spool valve 118. As shown in FIG.
(hereinafter referred to as the B state), the spool valve is moved by discharging the downstream pressure from the orifice 122 by the opening operation (during excitation) of the solenoid valve 28. When the action of the line oil pressure on 124 is removed, the centerline CS
As shown on the left side, the spool valve element 124 is in a state (hereinafter referred to as the A state) in which it is moved according to the urging force of the spring 126. That is, the spool valve element 124 is placed in the second position in response to the operation of the solenoid valve 28, and in state B, the line oil passage 72 and the supply passage 128 are connected, while the discharge passage 130 is blocked. In state A, the line hydraulic pressure is allowed to be supplied to the primary hydraulic cylinder 44, and the pressure within the primary hydraulic cylinder 44 is increased. Discharge passage 1
30 is opened to the drain pipe 131, and the supply of line supply hydraulic pressure to the primary side hydraulic cylinder 44 is blocked, and the primary side hydraulic cylinder 44
The pressure inside is reduced. Here, the spool valve 124 is connected to the spool shaft 13.
2 and a plurality of spool land portions 134A, 134B partially formed with a large diameter in the axial direction.
134S, and is slidably fitted into a cylinder bore 138 formed in the valve body 136, and when the spool valve element 124 is in the B state, the spool land portion 134B is connected to the line oil passage 7.
When the spool valve 124 is in the A state, the spool land portion 124A partially opens the port that communicates with the discharge passage 130 and opens into the cylinder bore 138. It is designed to open.
That is, by setting the movement stroke of the spool valve element 124 short, the responsiveness of the switching operation is enhanced. In addition, line oil path 7
2 and the spool valve 118
Reference numeral 40 sets the maximum flow rate of hydraulic oil supplied to the hydraulic cylinder 44. On the other hand, the solenoid valve 30 is also equipped with an orifice 142, and like the solenoid valve 30, when the solenoid valve 30 is closed (de-energized), the spool valve 120 is spool valve 14
The spool valve 144 is moved against the biasing force of the spring 146 (hereinafter referred to as state B) by applying line hydraulic pressure through the orifice 142 to the end face of the spool valve 144, but when it is released, the center line Spool valve 144 as shown on the left side of CH
The action of the line hydraulic pressure is released and the spool valve element 144 is moved according to the biasing force of the spring 146 (hereinafter referred to as the A state). The spool valve 120 is equipped with a downstream supply port 148 and an upstream discharge port 150 that communicate with the primary hydraulic cylinder 44, and an upstream supply port 152 and a downstream discharge port that are connected to the supply passage 128 and the discharge passage 130, respectively. A side discharge port 154 is provided, and when the spool valve element 144 is brought into the B state by the closing operation (when not energized) of the solenoid valve 30, a downstream side supply port 148 and an upstream side supply port 152 are provided. The upstream discharge port 150 and the downstream discharge port 154 are communicated with each other. Also,
When the spool valve 144 is placed in the A state according to the opening operation (at the time of excitation) of the solenoid valve 30, the upstream discharge port 150 and the downstream discharge port 154 are cut off, and the upstream supply port 15
2 and the downstream supply port 148 are communicated with each other. Here, the spool valve 144 has a throttle passage 15.
6 is formed to penetrate in the axial direction (thickness direction) through a spool land portion 160A, which will be described later. A small amount of hydraulic oil is allowed to flow through the throttle passage 156. The flow rate of the hydraulic oil is set to be equal to or higher than the leakage rate from the hydraulic cylinder 44, for example. Further, the spool valve 144 is connected to the spool shaft 15.
8 and spool land portions 160A, 160B, 160 partially formed with large diameters in the axial direction.
C, 160D, and are slidably fitted into the cylinder bore 138 formed in the valve body 136, and the spool valve element 144 is moved from A to B.
When the state is reached, the spool land portion 160B passes through the upstream discharge port 150 to partially open it (about half in the figure), and the spool valve 14
4 is in the A state again, the spool land portion 16
0A is allowed to pass through downstream supply port 148 to partially open it. That is, by setting the stroke of the spool valve element 144 short enough to partially open each port 148, 150 when opening or closing each port, the responsiveness of the switching operation of the spool valve 120 is enhanced. The spool land section 160A functions as a supply side spool land section since it exclusively opens and closes the distribution path of hydraulic oil supplied to the hydraulic cylinder 44, and the spool land section 160B exclusively opens and closes the distribution path of hydraulic oil supplied to the hydraulic cylinder 44.
It functions as a discharge side spool land part because it opens and closes the flow path of the hydraulic oil discharged from 4. In addition, the hydraulic cylinder 44 and the upstream discharge port 1
The throttle 162 provided in the discharge passage 161 on the upstream side between the hydraulic cylinder 44 and the hydraulic cylinder 50 is for setting the maximum flow rate of the hydraulic oil discharged from the hydraulic cylinder 44 . In addition, in the solenoid valves 28 and 30, spool valves 118 and 120 are located on the left and right of the center line.
The operating states corresponding to the operating positions shown on the left and right of the center lines CS and CH are shown. Furthermore, each port in the spool valves 118 and 120 is in a half-open state, but if the width and diameter of the annular groove connected to the port are set large to ensure the flow area, the flow resistance will be lowered, which is a practical problem. Not. In the hydraulic system 12 configured as described above, for example, the present applicant has previously filed a patent application filed in 1983-
The hydraulic control method described in the specification of No. 203130 is the first
It is carried out as shown in the table. That is, when the CVT 10 is to be upshifted rapidly, the drive signal SD1 that de-energizes the solenoid valve 28 is output from the gear ratio controller 14, and the spool valve 12 of the shift switching valve device 58 is outputted from the gear ratio controller 14.
At the same time, the drive signal SD2 for energizing the electromagnetic valve 30 is output from the gear ratio controller 14, and the spool valve element 144 of the shift speed control valve device 60 is placed in the A state. Therefore, as shown in FSmax in FIG.
of

[Table] A large amount of oil is then supplied to the hydraulic cylinder 44, and the effective diameter of the primary variable pulley 24 is rapidly increased, and the effective diameter of the secondary variable pulley 26 is rapidly decreased. As a result, the gear ratio of the CVT 10 is rapidly changed in the upshift direction. Here, the excitation state of the solenoid valve 30 indicates a state in which its duty is 100%. In the above upshift state, when slowly upshifting with the shift speed (speed ratio change speed) set to the minimum, the drive signal SD2 that de-energizes the solenoid valve 30 is output from the speed ratio controller 14, so that the shift speed control valve The spool valve 144 in the device 60 is in the B state. Therefore, the hydraulic oil supplied from the line oil passage 72 to the hydraulic cylinder 44 passes through the throttle passage 156 formed in the spool valve element 144, as shown in FIG.
As shown by FSmin, the amount of hydraulic oil supplied to the hydraulic cylinder 44 is significantly suppressed. As a result,
The speed at which the gear ratio changes in the upshift direction of the CVT 10 is significantly slowed down. Here, the non-excited state of the solenoid valve 30 indicates a state where its duty is 0%. In the above-mentioned upshift state, if the speed ratio change speed is desired to be an intermediate shift speed between the above two states, the pulse-shaped drive signal SD2 for energizing the solenoid valve 30 at a predetermined period is used to shift the gear ratio. It is supplied from the ratio controller 14, and the spool valve element 144 of the shift speed control valve device 60 is periodically positioned between the A state and the B state with a predetermined duty. Therefore, as shown in FIG. 7, the flow rate of hydraulic oil supplied to the hydraulic cylinder 44 is reduced by
It is continuously controlled by changing the duty of 0. On the other hand, when it is desired to rapidly downshift the CVT 10, a drive signal SD1 for energizing the solenoid valve 28 is output from the gear ratio controller 14, and the spool valve 1 in the shift switching valve device 58 is outputted from the gear ratio controller 14.
24 is placed in the A state, and a drive signal SD2 that de-energizes the solenoid valve 30 is output from the gear ratio controller 14, and the spool valve element 144 of the shift speed control valve device 60 is placed in the B state. For this reason, the spool valve 14 inside the hydraulic cylinder 44
4 is considered to be the B state. For this reason, in Figure 8
As shown in FDmax, the hydraulic oil in the hydraulic cylinder 144 flows through the upstream discharge port 15 to the throttle 162.
0, downstream discharge port 154, discharge passage 130,
It is rapidly discharged through the drain pipe 131, and the effective diameter of the primary variable pulley 24 is rapidly reduced, and the effective diameter of the secondary variable pulley 26 is rapidly increased. As a result, the CVT 10 is rapidly shifted in the downshift direction. On the other hand, in the case of a slow downshift, a drive signal SD2 for energizing the solenoid valve 30 is output from the gear ratio controller 14,
The spool valve 144 in the shift speed control valve device 60 is placed in the A state. Therefore, the space between the upstream discharge port 150 and the downstream discharge port 154 is closed by the spool land portion 160A, but as shown in FDmin in FIG. A small amount of hydraulic oil in the hydraulic cylinder 44 leaks from the gap 159 between the two, so that the effective diameter of the primary variable pulley 24 is gradually reduced, and the CVT 10 is slowly downshifted. In the downshift state as described above, when the shift speed is set to an intermediate speed between the above two states, the pulsed drive signal SD2 for energizing the solenoid valve 30 at a predetermined period is transmitted to the gear ratio controller 14. output from the shift speed control valve device 6
0 spool valve 144 is repeatedly positioned in the A state and the B state. As a result, as the duty of the electromagnetic valve 30 is continuously changed as shown by the solid line in FIG. 8, the discharge flow rate of the hydraulic oil from the hydraulic cylinder 44 is continuously controlled. As described above, when the CVT 10 is upshifted and downshifted, the supply flow rate of hydraulic oil supplied to the hydraulic cylinder 44 or the discharge flow rate of hydraulic oil discharged from the hydraulic cylinder 44 is continuously controlled, so that, for example, This allows the actual engine speed to match the target engine speed. Here, in the shift speed control valve device 60, as described above, the spool valve element 144 is set in the B state where the upstream side discharge port 150 is partially opened and the A state where the downstream side supply port 148 is partially opened.
Since the moving stroke is determined to be short, high responsiveness of the switching operation in the shift speed control valve device 60 can be obtained, and in the duty control of repeatedly operating the solenoid valve 30, the range in which the flow rate can be controlled in response to changes in duty is as shown in FIGS. Figure 8
As shown in CWS and CWD, the widths are significantly expanded compared to the conventional widths CWS' and CWD' in which the ports are fully opened, allowing for fine-grained, high-precision control. Further, according to this embodiment, the spool valve 144
As a result of the shortened travel stroke, the shift speed control valve device 60 has the advantage of having a smaller shape and reduced weight and manufacturing cost. Furthermore, there is an advantage that the tolerance of the spring constant of the spring 146 can be relaxed by reducing the movement stroke of the spool valve element 144. Further, according to this embodiment, even if the opening is partially opened by the spool land portion in the flow-permitting state of the shift speed control valve device 60, the throttle passage 156 provided in the supply side spool land portion 160A and Since the hydraulic oil is supplied to the hydraulic cylinder 44 through the upstream discharge port 150, the flow rate during the rapid speed change is ensured, and a sufficient speed change can be obtained. In addition, each valve 64, 66, 58 in FIG.
A part or all of 60 etc. may be provided in a common housing. The above-mentioned embodiment is merely one embodiment of the present invention, and various modifications may be made to the present invention without departing from its accuracy.

[Brief explanation of the drawing]

FIG. 1 is an explanatory diagram illustrating a hydraulic system for a belt-type continuously variable transmission and its control system to which the present invention is applied. FIG. 2 is a diagram illustrating the main part of FIG. 1. FIG. 3 is a sectional view of a main part of the hydraulic system shown in FIGS. 1 and 2 for explaining in more detail the structure of the hydraulic system. FIG. 4 is a diagram showing the relationship between the speed ratio pressure signal output from the sensing valve of FIG. 3 and the amount of movement of the movable rotating body. FIG. 5 is a diagram showing the relationship between the throttle pressure signal output from the throttle valve of FIG. 3 and the throttle opening. FIG. 6 is a diagram showing the relationship between the line oil pressure adjusted by the regulator valve of FIG. 3 and the throttle opening. 7 and 8 are diagrams respectively showing the change characteristics of the supply flow rate or the discharge flow rate with respect to changes in the duty of the signal that drives the electromagnetic valve in the shift speed control valve device of FIG. 3. 10... Belt type continuously variable transmission (CVT), 12...
...Hydraulic system, {24...Primary side variable pulley, 26
...Secondary side variable pulley} (variable pulley), 36...
Transmission belt, 44... (primary side) hydraulic cylinder,
58...Shift switching valve device, 60...Shift speed control valve device, 128...Supply passage, 130, 16
1...Discharge passage, 144...Spool valve, 16
0A... Spool land part (supply side spool land part), 160B... Spool land part (discharge side spool land part), 148... Downstream supply port, 150... Upstream discharge port, 152... Upstream supply Port, 154...downstream discharge port,
156...Aperture passage.

Claims (1)

[Scope of Claims] 1. A belt-type continuously variable gear ratio that changes the gear ratio by supplying hydraulic oil to a hydraulic cylinder for changing the effective diameter of a variable pulley or by allowing discharge of hydraulic oil from within the hydraulic cylinder. In a transmission, a shift switching valve device is driven to two positions: a state where hydraulic oil is allowed to be supplied to the hydraulic cylinder and a state where hydraulic oil in the hydraulic cylinder is allowed to be discharged. , which is inserted between the shift switching valve device and the hydraulic cylinder, and has a state of allowing and a state of inhibiting the flow of hydraulic oil supplied to the hydraulic cylinder or hydraulic oil discharged from the hydraulic cylinder. a shift speed control valve device driven to two positions, the shift speed control valve device comprising: an upstream supply port to which hydraulic fluid is exclusively supplied from the shift switching valve device; The hydraulic oil in the cylinder is connected to the shift switching valve via a downstream discharge port for exclusively sending out the hydraulic oil to the shift switching valve device, and the hydraulic oil supplied to the upstream supply port passage is transferred to the hydraulic cylinder. and an upstream discharge port for receiving hydraulic fluid in the hydraulic cylinder, respectively, between the upstream supply port and the downstream supply port. A supply spool land section that opens and closes, and a discharge spool land section that opens and closes between the upstream discharge port and the downstream discharge port are provided. It has a spool valve that can be operated between two positions, a permissive side position and a flow restricting side position, and the supply side spool land portion has a spool valve that is connected to the upstream side supply port and the downstream side. When closing the gap between the upstream supply port and the downstream supply port, the flow rate of hydraulic oil from the upstream supply port to the downstream supply port is suppressed, and the supply spool land portion is located between the upstream supply port and the downstream supply port. A throttle passage is provided that guides hydraulic fluid from the upstream supply port to the upstream discharge port when opened, and at least the flow-permitting side position of the two positions of the spool valve element is connected to the spool valve. For a belt-type continuously variable transmission characterized in that the supply side spool land part and the discharge side spool land part of the child are set at positions where their openings are partially opened to allow the flow of hydraulic oil, respectively. Hydraulic equipment.