JP2009257538A - Belt-type continuously variable transmission and transmission controller - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To prevent an increase in fuel consumption of an internal combustion engine. <P>SOLUTION: The belt-type continuously variable transmission comprises a working fluid confining means for inhibiting changeover of inhibition of a discharge of the working fluid from a pulley hydraulic chamber based on decreasing amount in the temperature of the working fluid in the pulley hydraulic chamber, that is, the decreasing amount in the temperature of the working fluid starting at changeover from inhibition of the discharge of the working fluid in the pulley hydraulic chamber into allowance of the discharge of the working fluid in the pulley hydraulic chamber. Thereby the belt-type continuously variable transmission prevents the increase in fuel consumption of the internal combustion engine. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a belt type continuously variable transmission and a transmission control device, and more particularly to a belt type continuously variable transmission and a transmission control device in which a gear ratio is adjusted by the pressure of hydraulic oil in a hydraulic chamber.

  2. Description of the Related Art Conventionally, there is a belt type continuously variable transmission in which hydraulic oil is supplied to a hydraulic chamber and a gear ratio is adjusted by the pressure of the hydraulic oil. For example, Patent Document 1 discloses that a supply-side valve that permits the supply of hydraulic oil from the outside of the hydraulic chamber to the hydraulic chamber, and the movable sheave from the hydraulic chamber to the outside when the position in the axial direction with respect to the fixed sheave is constant. Discloses a belt-type continuously variable transmission including a discharge-side control valve that prohibits the discharge of hydraulic oil.

JP 2006-300270 A, paragraph number 0008

  Patent Document 1 discloses and suggests a specific case of switching between prohibiting and permitting the discharge of hydraulic oil from the hydraulic chamber, in addition to the case where the axial position of the movable sheave with respect to the fixed sheave is constant. Absent. However, depending on the case of switching between prohibiting and permitting the discharge of hydraulic oil from the hydraulic chamber, there is a possibility that an increase in fuel consumption of the internal combustion engine cannot be sufficiently suppressed.

  For example, if frequent switching between prohibiting and permitting the discharge of hydraulic oil from the hydraulic chamber occurs, the power required to switch between prohibiting and permitting the discharge of hydraulic oil from the hydraulic chamber increases. Here, usually, the power is obtained from the rotation taken out from the internal combustion engine. As a result, the conventional belt-type continuously variable transmission may not sufficiently suppress the increase in fuel consumption of the internal combustion engine if frequent switching between prohibition and permission of discharge of hydraulic oil from the hydraulic chamber occurs. There is.

  The present invention has been made in view of the above, and an object thereof is to suppress an increase in fuel consumption of an internal combustion engine.

  In order to solve the above-described problems and achieve the object, a belt-type continuously variable transmission according to the present invention includes a shaft that receives rotation input from an internal combustion engine and rotates about a rotation shaft, and the shaft. A fixed sheave coupled and rotating about the rotation axis; a movable sheave provided on the shaft opposite to the fixed sheave and moving on the shaft in the direction of the rotation axis; and provided on the shaft; A pulley hydraulic chamber that applies a force in the direction of the rotation axis to the movable sheave by the pressure of the hydraulic oil; and a decrease in the temperature of the hydraulic oil in the pulley hydraulic chamber, the hydraulic oil in the pulley hydraulic chamber being Based on the amount of decrease in the temperature of the hydraulic oil starting from the time when the hydraulic oil in the pulley hydraulic chamber is switched from a state in which the discharge is prohibited to a state in which the hydraulic oil is allowed to be discharged, Means confinement hydraulic oil inhibits the switching to the state in which the discharge of the hydraulic fluid from over Li hydraulic chamber is inhibited, characterized in that it comprises a.

  In the belt type continuously variable transmission according to the present invention, the pulley is switched from the state in which the discharge of the hydraulic oil from the pulley hydraulic chamber is prohibited to the state in which the discharge of the hydraulic oil from the pulley hydraulic chamber is permitted. When the amount of decrease in the temperature of the hydraulic oil in the hydraulic chamber is insufficient, switching to a state in which the discharge of hydraulic oil from the pulley hydraulic chamber to the outside of the pulley hydraulic chamber is prohibited is prohibited. In other words, the belt type continuously variable transmission according to the present invention is prohibited from discharging the hydraulic oil from the pulley hydraulic chamber to the outside of the pulley hydraulic chamber only when the temperature drop of the hydraulic oil in the pulley hydraulic chamber is sufficient. Allows switching to the active state.

  Here, when the amount of decrease in the temperature of the hydraulic oil in the pulley hydraulic chamber is sufficient, even if the hydraulic oil is confined again in the pulley hydraulic chamber, the time until the temperature of the hydraulic oil exceeds the appropriate temperature in the pulley hydraulic chamber Is sufficient. Here, when sufficient time can be secured until the temperature of the hydraulic oil exceeds the appropriate temperature in the pulley hydraulic chamber, switching between permitting and prohibiting the discharge of hydraulic oil from the pulley hydraulic chamber frequently occurs. This is a case where this can be suppressed.

  Thereby, the belt type continuously variable transmission according to the present invention can suppress a decrease in time until the temperature of the hydraulic oil in the pulley hydraulic chamber exceeds an appropriate temperature. Therefore, the belt-type continuously variable transmission according to the present invention can suppress frequent occurrence of switching between permitting and prohibiting the discharge of hydraulic oil from the pulley hydraulic chamber. As a result, the belt-type continuously variable transmission according to the present invention can suppress an increase in fuel consumption of the internal combustion engine that generates rotation input to the shaft.

  As a preferred aspect of the present invention, it is desirable that the hydraulic oil confining means estimates a decrease in the temperature of the hydraulic oil from the starting point based on a time elapsed from the starting point.

  As a preferred aspect of the present invention, the hydraulic oil confining means is configured to reduce the temperature of the hydraulic oil from the starting point based on the flow rate of the hydraulic oil guided to the pulley hydraulic chamber after the starting point. It is desirable to estimate the quantity.

  As a preferred aspect of the present invention, the hydraulic oil confining means may estimate the amount of decrease in the hydraulic oil temperature from the starting point based on the temperature of the hydraulic oil guided to the pulley hydraulic chamber. desirable.

  As a preferred aspect of the present invention, the hydraulic oil confining means is disposed in the pulley hydraulic chamber after the amount of decrease in the temperature of the hydraulic oil estimated based on the time elapsed from the calculation point and after the calculation point. The hydraulic oil estimated based on the amount of decrease in the temperature of the hydraulic oil estimated based on the flow rate of the introduced hydraulic oil, and the flow rate of hydraulic oil introduced to the pulley hydraulic chamber after the starting point It is desirable to prohibit switching to a state in which the discharge of the hydraulic oil from the pulley hydraulic chamber is prohibited based on the amount of decrease in temperature of the pulley.

  In order to solve the above-described problems and achieve the object, a transmission control device according to the present invention is connected to a shaft that receives rotation input from an internal combustion engine and rotates about a rotation shaft, and the shaft. A fixed sheave that rotates about the rotation shaft, a movable sheave that is provided on the shaft so as to face the fixed sheave and moves on the shaft in the direction of the rotation axis, and a movable sheave that is provided on the shaft. A transmission control device that controls a belt-type continuously variable transmission that includes a pulley hydraulic chamber that applies a force in the rotation axis direction to the sheave by the pressure of the hydraulic oil, and the temperature of the hydraulic oil in the pulley hydraulic chamber When the hydraulic oil in the pulley hydraulic chamber is prohibited from being discharged and the hydraulic oil in the pulley hydraulic chamber is allowed to be discharged. It was starting point on the basis of the decrease in the temperature of the hydraulic oil, discharged of the working oil from the pulley hydraulic chamber and inhibits the switching to the condition to be inhibited.

  The transmission control device according to the present invention allows the hydraulic oil in the pulley hydraulic chamber to be discharged when the hydraulic oil is permitted to be discharged from the pulley hydraulic chamber from the state where the hydraulic oil is not discharged from the pulley hydraulic chamber. When the amount of temperature decrease is sufficient, discharge of hydraulic oil from the pulley hydraulic chamber to the outside of the pulley hydraulic chamber is permitted.

  Thereby, the transmission control device according to the present invention can suppress a decrease in time until the temperature of the hydraulic oil in the pulley hydraulic chamber exceeds an appropriate temperature. Therefore, the transmission control apparatus according to the present invention can suppress frequent occurrence of switching between permitting and prohibiting the discharge of hydraulic oil from the pulley hydraulic chamber. As a result, the transmission control device according to the present invention can suppress an increase in fuel consumption of the internal combustion engine that generates rotation input to the shaft.

  The belt type continuously variable transmission and the transmission control device according to the present invention can suppress an increase in fuel consumption of the internal combustion engine.

  Hereinafter, the present invention will be described in detail with reference to the drawings. The present invention is not limited by the best mode for carrying out the invention (hereinafter referred to as an embodiment). In addition, constituent elements in the following embodiments include those that can be easily assumed by those skilled in the art, those that are substantially the same, and those in a so-called equivalent range.

  FIG. 1 is a conceptual diagram showing an overall configuration of a power transmission portion of a vehicle provided with a belt type continuously variable transmission according to the present embodiment. As shown in FIG. 1, the power transmission mechanism of the vehicle 100 includes a belt-type continuously variable transmission 110, an internal combustion engine 120, a torque converter 130, a forward / reverse switching mechanism 140, a reduction gear 150, and a differential device 160. And comprising.

  The internal combustion engine 120 outputs rotation from a crankshaft 121 that reciprocates in the central axis direction of a cylinder formed in a cylindrical shape and converts the reciprocating motion of the piston into rotational motion.

  The internal combustion engine 120 is not limited to a so-called reciprocating internal combustion engine including a piston and a cylinder. The internal combustion engine 120 only needs to output a rotational force. For example, the internal combustion engine 120 may be a rotary internal combustion engine or a motor.

  The torque converter 130 is a kind of fluid clutch, and transmits the rotation extracted from the internal combustion engine 120 to the forward / reverse switching mechanism 140 via hydraulic oil. The torque converter 130 amplifies the torque extracted from the internal combustion engine 120.

  The forward / reverse switching mechanism 140 switches the rotation direction of the rotation from the torque converter 130 and transmits the rotation to the belt type continuously variable transmission 110.

  The belt type continuously variable transmission 110 changes the rotational speed of the rotation input from the forward / reverse switching mechanism 140 to a desired rotational speed and outputs it. A detailed description of the belt type continuously variable transmission 110 will be described later.

  The reduction gear 150 reduces the rotation speed of the rotation from the belt type continuously variable transmission 110 and transmits the rotation to the differential device 160.

  The differential device 160 absorbs the difference in rotational speed between the center wheel of the turn, that is, the inner wheel 180 and the outer wheel 180 that occurs when the vehicle 100 turns.

  The power transmission mechanism of the vehicle 100 is formed by the above components. The rotation extracted from the internal combustion engine 120 is transmitted to the torque converter 130 via the crankshaft 121. The rotation whose torque is amplified by the torque converter 130 is transmitted to the forward / reverse switching mechanism 140 via an input shaft 131 as an input shaft of the belt type continuously variable transmission 110.

  The rotation whose rotation direction is switched by the forward / reverse switching mechanism 140 is transmitted to the belt-type continuously variable transmission 110 via the primary shaft 51 as the input shaft. The rotation whose rotation speed is changed by the belt-type continuously variable transmission 110 is transmitted to the speed reduction device 150.

  The rotation decelerated by the reduction gear 150 is transmitted to the differential gear 160 via the final drive pinion 151 of the reduction gear 150 and the ring gear 161 of the differential gear 160 meshing with the final drive pinion 151.

  The rotation transmitted to the differential device 160 is transmitted to the drive shaft 170. A wheel 180 is attached to the drive shaft 170 opposite to the differential device 160 side. The rotation transmitted to the drive shaft 170 is transmitted to the wheel 180. Thereby, the wheel 180 rotates, and the vehicle 100 travels when the wheel 180 transmits the rotation to the road surface.

  The belt type continuously variable transmission 110 includes a primary pulley 50, a secondary pulley 60, and a belt 80. Belt type continuously variable transmission 110 receives rotation input to primary pulley 50. The rotation input to the primary pulley 50 is transmitted to the secondary pulley 60. At this time, the rotation speed is adjusted.

  The rotation transmitted to the secondary pulley 60 is transmitted to the speed reducer 150. A value obtained by dividing the rotational speed of the primary shaft 51 as the input shaft by the rotational speed of the secondary shaft 61 as the output shaft is referred to as a gear ratio. Also, changing the gear ratio is hereinafter referred to as a gear change.

  FIG. 2 is a cross-sectional view showing the primary pulley according to the present embodiment. In the belt type continuously variable transmission 110, the primary pulley 50 and the secondary pulley 60 are configured in substantially the same manner. Therefore, in this embodiment, the primary pulley 50 will be mainly described.

  The primary pulley 50 includes a primary shaft 51, a primary fixed sheave 52, a primary movable sheave 53, a primary pulley hydraulic chamber 54, a spline 55, and a primary partition wall 56. As shown in FIGS. 1 and 2, the primary shaft 51 is supported by a bearing 81 and a bearing 82 so as to be rotatable coaxially with the rotation shaft of the input shaft 131. Here, as shown in FIG. 1, the secondary shaft 61 is supported by a bearing 83 and a bearing 84 so as to be rotatable in parallel with the primary shaft 51.

  The primary shaft 51 is formed in a cylindrical shape. As shown in FIG. 2, the primary shaft 51 rotates about the rotation axis RL. The primary fixed sheave 52 is usually formed integrally with the primary shaft 51. The primary fixed sheave 52 may be formed separately from the primary shaft 51 and fixed to the primary shaft 51. Thus configured, the primary fixed sheave 52 rotates integrally with the primary shaft 51 around the rotation axis RL. Here, a direction orthogonal to the rotation axis RL is referred to as a radial direction. The primary fixed sheave 52 is formed to protrude in the radial direction from the outer periphery of the primary shaft 51.

  Primary movable sheave 53 is formed separately from primary shaft 51. The primary movable sheave 53 has a through hole into which the primary shaft 51 is fitted. A spline 55 is formed on the inner peripheral surface of the through hole. Primary movable sheave 53 is fitted and attached to primary shaft 51 via spline 55. The primary movable sheave 53 is fitted into the primary shaft 51 so as to face the primary fixed sheave 52.

  The spline 55 supports the primary movable sheave 53 so that the primary movable sheave 53 can slide on the primary shaft 51 along the rotation axis RL of the primary shaft 51. In addition, the spline 55 transmits rotation about the rotation axis RL from the primary shaft 51 to the primary movable sheave 53. Therefore, the primary movable sheave 53 slides and moves on the primary shaft 51 by the spline 55 and rotates integrally with the primary shaft 51.

  A substantially V-shaped primary groove 80 a is formed between the primary fixed sheave 52 and the primary movable sheave 53. Further, as the primary movable sheave 53 slides on the primary shaft 51, the distance between the primary fixed sheave 52 and the primary movable sheave 53 changes. Here, as shown in FIG. 1, the secondary pulley 60 is also formed with a secondary groove 80b similar to the primary groove 80a.

  A belt 80, which is a metal endless belt, is wound between the primary groove 80a and the secondary groove 80b. The belt 80 transmits the rotation of the primary pulley 50 to the secondary pulley 60.

  As shown in FIG. 2, the primary pulley hydraulic chamber 54 is a space formed by being surrounded by a primary shaft 51, a primary movable sheave 53, and a primary partition wall 56. The primary partition 56 is formed having a through hole. The primary partition wall 56 is provided on the primary shaft 51 by fitting the primary shaft 51 into the through hole. The primary partition wall 56 is provided on the side opposite to the primary fixed sheave 52 side with the primary movable sheave 53 as a boundary.

  The primary pulley hydraulic chamber 54 pushes the primary movable sheave 53 toward the primary fixed sheave 52 side by the hydraulic oil supplied to the primary pulley hydraulic chamber 54. Accordingly, the primary movable sheave 53 is pushed toward the primary fixed sheave 52 side along the primary shaft 51. As a result, the primary pulley hydraulic chamber 54 generates a clamping pressure with respect to the belt 80 wound around the primary groove 80a.

  When the distance between the primary movable sheave 53 and the primary fixed sheave 52 changes due to the clamping pressure, the distance between the secondary fixed sheave 62 and the secondary movable sheave 63 included in the secondary pulley 60 also changes so as to keep the tension of the belt 80 constant. To do. Thereby, the contact radius of the belt 80 with respect to the primary pulley 50 and the contact radius of the belt 80 with respect to the secondary pulley 60 change. Thus, belt type continuously variable transmission 110 shifts the rotation extracted from internal combustion engine 120.

  The primary shaft 51 has a first oil passage OL01. The first oil passage OL01 has one end connected to an oil tank OT that is a supply source of hydraulic oil, and the other end opened to the primary pulley hydraulic chamber 54. As a result, the first oil passage OL01 allows hydraulic oil to flow between the oil tank OT and the primary pulley hydraulic chamber 54. The first oil passage OL01 includes a plurality of axial oil passages OL01a formed in a direction along the rotation axis RL of the primary shaft 51, and a plurality of radial oil passages OL01b formed in a direction orthogonal to the rotation shaft RL. It is formed including.

  On the path of the first oil path OL01, in order from the oil tank OT to the primary pulley hydraulic chamber 54, an oil pump OP, a gear ratio control side regulator ORa, and a hydraulic oil confinement device as hydraulic oil confinement means. 10 are provided. The oil pump OP sends hydraulic oil from the oil tank OT toward the primary pulley hydraulic chamber 54.

  Here, the oil pump OP obtains power for operating from the crankshaft 121. Therefore, when the power consumed by the oil pump OP increases, the energy that the crankshaft 121 has is consumed. In order to compensate for this energy consumption, the internal combustion engine 120 increases the fuel injection amount. Thus, when the power consumed by the oil pump OP increases, the amount of fuel consumed by the internal combustion engine 120 increases.

  An object of the present embodiment is to suppress an increase in power consumed by the oil pump OP and suppress an increase in fuel consumption of the internal combustion engine 120. The increase in the amount of fuel consumed by the internal combustion engine 120 is equivalent to the deterioration of fuel consumption. That is, the belt type continuously variable transmission 110 suppresses deterioration of fuel consumption by suppressing an increase in power consumed by the oil pump OP.

  The gear ratio control side regulator ORa adjusts the pressure of the hydraulic oil supplied to the primary pulley hydraulic chamber 54. Further, the gear ratio control side regulator ORa is electrically connected to the ECU 40. The gear ratio control side regulator ORa returns the hydraulic oil to the oil tank OT when the hydraulic oil is discharged from the primary pulley hydraulic chamber 54.

  The hydraulic oil confinement device 10 is a device that controls the discharge of hydraulic oil from the primary pulley hydraulic chamber 54. The hydraulic oil confinement device 10 prohibits the discharge of hydraulic oil from the primary pulley hydraulic chamber 54 for a predetermined period. A state in which the discharge of hydraulic oil from the primary pulley hydraulic chamber 54 is prohibited is referred to as a closed state. In addition, a state in which the discharge of hydraulic oil from the primary pulley hydraulic chamber 54 is permitted is referred to as an open state.

  FIG. 3 is an enlarged cross-sectional view of the hydraulic oil confining device when the primary pulley hydraulic chamber is confined. FIG. 4 is an enlarged cross-sectional view of the hydraulic oil confining device with the primary pulley hydraulic chamber open. Hereinafter, an example of the hydraulic oil confining device 10 will be described.

  The hydraulic oil confinement device 10 includes a piston operation hydraulic chamber 11, a seal portion 12, a valve body 13, a piston 14, and a spring 15. The piston operating hydraulic chamber 11 applies a pressing force to the piston 14 by the pressure of the hydraulic oil in the piston operating hydraulic chamber 11. The seal portion 12 is formed having a tapered surface 12a in the first oil passage OL01. As the taper surface 12a approaches the primary pulley hydraulic chamber 54, the distance between the taper surfaces facing each other increases.

  The seal part 12 has an opening 12b. The hydraulic oil moves back and forth through the seal 12 through the opening 12b. The valve body 13 is formed in a spherical shape. The diameter of the valve body 13 is larger than the diameter of the opening 12b. The valve body 13 contacts the tapered surface 12a of the seal portion 12 from the primary pulley hydraulic chamber 54 side. Thereby, the valve body 13 closes the opening 12b from the primary pulley hydraulic chamber 54 side.

  The piston 14 includes a pressure receiving surface 14a and a rod-like portion 14b. The pressure receiving surface 14 a is disposed in the piston operating hydraulic chamber 11. The rod-like portion 14b is disposed in the first oil passage OL01. One end of the rod-like portion 14b is connected to the pressure receiving surface 14a. Further, the other end of the rod-like portion 14b passes through the opening 12b and comes into contact with or connected to the valve body 13. Accordingly, when the piston 14 moves in a direction approaching the valve body 13 due to the pressure of the hydraulic oil in the piston operating hydraulic chamber 11, the piston 14 pushes the valve body 13 in a direction away from the seal portion 12.

  The spring 15 applies a force in a direction away from the valve body 13 to the piston 14. The force is the minimum force necessary for returning the piston 14 to the previous state after moving in the direction approaching the valve body 13, that is, the closed state shown in FIG.

  Hydraulic oil is supplied to the piston operating hydraulic chamber 11. The hydraulic oil supply path will be described below. As shown in FIG. 2, the primary shaft 51 is formed with a first oil passage OL01 and another second oil passage OL02. One end of the second oil passage OL02 is connected to an oil tank OT that is a supply source of hydraulic oil, and the other end opens to the piston operating hydraulic chamber 11. As a result, the second oil passage OL02 allows hydraulic oil to flow between the oil tank OT and the piston operating hydraulic chamber 11. The second oil passage OL02 includes a plurality of axial oil passages OL02a formed in a direction along the rotation axis RL of the primary shaft 51, and a plurality of radial oil passages OL02b formed in a direction orthogonal to the rotation shaft RL. It is formed including.

  On the path of the first oil passage OL01, an oil pump OP, a closing control side regulator ORb, and a hydraulic oil closing device 10 are provided in order from the oil tank OT toward the primary pulley hydraulic chamber 54. The oil pump OP sends hydraulic oil from the oil tank OT toward the piston operating hydraulic chamber 11.

  The closing control side regulator ORb adjusts the pressure of the hydraulic oil supplied to the piston operation hydraulic chamber 11. Further, the closing control side regulator ORb is electrically connected to an ECU 40 described later. The closing control side regulator ORb returns the hydraulic oil to the oil tank OT when the hydraulic oil is discharged from the piston operation hydraulic chamber 11.

  Here, as shown in FIG. 3, the area of the pressure receiving surface 14 a that receives the pressure of the hydraulic oil is defined as a pressure receiving area Ap. Moreover, the part which contacts the valve body 13 of the seal | sticker part 12 is circular, and let the said circular area be seal part area Acv. Further, the pressure of the hydraulic oil in the piston operation hydraulic chamber 11 is set as a hydraulic pressure Pcv, and the pressure of the hydraulic oil in the primary pulley hydraulic chamber 54 is set as a hydraulic pressure Ps. The force generated by the spring 15 is defined as a spring force Fsp. The relationship between the hydraulic pressures in the hydraulic chambers when the primary pulley hydraulic chamber 54 is closed and the relationship between the hydraulic pressures in the hydraulic chambers when the primary pulley hydraulic chamber 54 is open will be described below.

  In the closed state, the valve body 13 contacts the seal portion 12 as shown in FIG. As a result, the hydraulic oil discharge from the primary pulley hydraulic chamber 54 is prohibited by the hydraulic oil confining device 10 regardless of the magnitude of the hydraulic pressure Ps.

  When the primary pulley hydraulic chamber 54 is opened, the closing control is performed so that the product of the hydraulic pressure Pcv and the pressure receiving area Ap is greater than the product of the hydraulic pressure Ps and the seal area Acv plus the spring force Fsp. The hydraulic pressure Pcv is adjusted by the side regulator ORb. Thereby, the valve body 13 moves in the direction away from the seal part 12 by the piston 14, as shown in FIG. When the valve body 13 is separated from the seal portion 12, the hydraulic oil in the primary pulley hydraulic chamber 54 is discharged from the primary pulley hydraulic chamber 54 through the opening 12b.

  When the primary pulley hydraulic chamber 54 is open, the hydraulic oil flows through the gap between the valve body 13 and the tapered surface 12 a of the seal portion 12 toward the primary pulley hydraulic chamber 54. If the valve body 13 is separated from the seal portion 12 due to the flow of the hydraulic oil, the open state of the primary pulley hydraulic chamber 54 is maintained even if the piston 14 is separated from the valve body 13. That is, the belt type continuously variable transmission 110 does not require the hydraulic pressure Pcv to keep the primary pulley hydraulic chamber 54 open.

  In the belt type continuously variable transmission 110, when the primary pulley hydraulic chamber 54 is closed, the product of the hydraulic pressure Pcv and the pressure receiving area Ap is equal to the product of the hydraulic pressure Ps and the seal portion area Acv. The oil pressure Ps is adjusted by the closing control side regulator ORb so as to be equal to or less than the added value.

  Here, the valve body 13 is fitted in the opening 12 b of the seal portion 12. Therefore, the belt type continuously variable transmission 110 does not require the hydraulic pressure Pcv to keep the primary pulley hydraulic chamber 54 open. That is, the belt-type continuously variable transmission 110 requires hydraulic pressure when the primary pulley hydraulic chamber 54 is switched from the closed state to the open state, and when the primary pulley hydraulic chamber 54 is switched from the open state to the closed state.

  The hydraulic oil confinement device 10 is not limited to the above-described configuration. The hydraulic oil confining device 10 may be configured to prohibit the discharge of hydraulic oil from the primary pulley hydraulic chamber 54 for a predetermined period. For example, although the hydraulic oil confinement device 10 shown in FIG. 2 is provided in the primary partition wall 56, the installation location is not limited as long as it is on the first oil passage OL01. The hydraulic oil confinement device 10 may be provided on the primary shaft 51, for example.

  Here, in the case of the belt type continuously variable transmission 110 that does not include the hydraulic oil confining device 10, the pressure of the hydraulic oil in the primary pulley hydraulic chamber 54 is maintained when the transmission ratio of the belt type continuously variable transmission 110 is kept constant. The oil pump OP is operated to keep the pressure constant. However, in the present embodiment, when the primary pulley hydraulic chamber 54 is in the closed state, the pressure in the primary pulley hydraulic chamber 54 is kept constant without operating the oil pump OP. That is, the gear ratio of the belt type continuously variable transmission 110 is kept constant without operating the oil pump OP.

  Thereby, during the closed state, the belt type continuously variable transmission 110 reduces the power consumed by the oil pump OP. As a result, in the belt-type continuously variable transmission 110, an increase in fuel consumption of the internal combustion engine 120 is suppressed.

  However, there is a possibility that the following will be described as the time of the closed state of the primary pulley hydraulic chamber 54 becomes longer. In belt type continuously variable transmission 110, belt 80 and primary movable sheave 53 are in contact with each other. Here, when the belt-type continuously variable transmission 110 is in operation, the belt 80 undergoes a relative movement with respect to the primary movable sheave 53, that is, a so-called slip.

  By this sliding, frictional heat is generated between the primary movable sheave 53 and the belt 80. This frictional heat is transmitted to the hydraulic oil in the primary pulley hydraulic chamber 54 including the primary movable sheave 53 via the primary movable sheave 53.

  Further, the internal combustion engine 120 and the belt-type continuously variable transmission 110 are connected with metal members constituting each of them. As a result, the heat generated by the internal combustion engine 120 is transmitted to the belt-type continuously variable transmission 110 via the metal member. The heat transmitted from the internal combustion engine 120 to the belt type continuously variable transmission 110 is also transmitted to the hydraulic oil in the primary pulley hydraulic chamber 54 via the primary shaft 51, the primary partition wall 56, the primary movable sheave 53, and the like.

  As described above, the hydraulic oil receives the frictional heat and the heat generated by the internal combustion engine 120. As a result, the temperature of the hydraulic oil rises due to the heat. Hereinafter, the heat received by the hydraulic oil, such as the frictional heat and the heat generated by the internal combustion engine 120, is simply referred to as heat.

  When the primary pulley hydraulic chamber 54 is closed, the hydraulic oil in the primary pulley hydraulic chamber 54 is not discharged from the primary pulley hydraulic chamber 54. Further, when the primary pulley hydraulic chamber 54 is in the closed state, new hydraulic oil is not supplied into the primary pulley hydraulic chamber 54. Therefore, while the primary pulley hydraulic chamber 54 is in the closed state, the temperature of the hydraulic oil in the primary pulley hydraulic chamber 54 rises due to the heat without being cooled.

  When the temperature of the working oil rises, the working oil usually expands. Therefore, the hydraulic oil in the primary pulley hydraulic chamber 54 also expands when the temperature rises due to the heat. However, since the primary pulley hydraulic chamber 54 is in a closed state, when the temperature of the hydraulic oil in the primary pulley hydraulic chamber 54 increases, the pressure of the hydraulic oil in the primary pulley hydraulic chamber 54 increases.

  Therefore, when the temperature of the hydraulic oil rises while the primary pulley hydraulic chamber 54 is closed, the primary movable sheave 53 moves in a direction approaching the primary fixed sheave 52. That is, when the temperature of the hydraulic oil rises while the primary pulley hydraulic chamber 54 is closed, the speed ratio of the belt-type continuously variable transmission 110 deviates from the speed ratio targeted by the belt-type continuously variable transmission 110.

  Note that the speed ratio targeted by the belt-type continuously variable transmission 110 is a speed ratio calculated by the ECU 40 from the running conditions of the vehicle 100, and here, suppressing the fuel consumption of the internal combustion engine 120. This is the target gear ratio.

  As a result, the belt type continuously variable transmission 110 may increase the amount of fuel consumed by the internal combustion engine 120. Note that the speed ratio targeted by the belt type continuously variable transmission 110 is a speed ratio that should be the target of the belt type continuously variable transmission 110 calculated by the ECU 40 from the running conditions of the vehicle 100.

  In order to suppress an increase in the temperature of the hydraulic oil in the primary pulley hydraulic chamber 54, the primary pulley hydraulic chamber 54 may be opened. As a result, the hydraulic oil in the primary pulley hydraulic chamber 54 is discharged from the primary pulley hydraulic chamber 54, and new hydraulic oil is introduced into the primary pulley hydraulic chamber 54. That is, the hydraulic oil in the primary pulley hydraulic chamber 54 is replaced with new hydraulic oil.

  However, if the primary pulley hydraulic chamber 54 is opened unnecessarily, the following may occur. For example, the temperature of the hydraulic oil in the primary pulley hydraulic chamber 54 does not actually rise, and the primary pulley hydraulic pressure is changed to a time when replacement of the hydraulic oil in the primary pulley hydraulic chamber 54 is unnecessary, that is, a time that is not optimal. There is a risk of opening the chamber 54. As a result, the primary pulley hydraulic chamber 54 may be frequently switched between a closed state and an open state.

  If the primary pulley hydraulic chamber 54 is frequently switched between the closed state and the open state, the oil pump OP is operated by the amount of hydraulic pressure required to switch the primary pulley hydraulic chamber 54 between the closed state and the open state. Increases the power required for As a result, the belt type continuously variable transmission 110 may not be able to sufficiently suppress the fuel consumption of the internal combustion engine 120.

  Further, if the primary pulley hydraulic chamber 54 is frequently switched between the closed state and the open state, the number of movements of the piston 14 increases. Then, the number of collisions between the rod-shaped portion 14b and the valve body 13 also increases, and the valve body 13 may be worn and deformed. Further, due to the collision between the valve body 13 and the seal portion 12, the valve body 13 and the seal portion 12 may be worn and the valve body 13 and the seal portion 12 may be deformed.

  Thereby, the belt type continuously variable transmission 110 has an unexpected gap between the valve body 13 and the seal portion 12. The hydraulic oil flows through this gap, and the belt-type continuously variable transmission 110 cannot be kept properly closed.

  As a result, the belt-type continuously variable transmission 110 increases the amount of deviation between the actual gear ratio and the target gear ratio of the belt-type continuously variable transmission 110, and the power required to operate the oil pump OP is increased. To increase. As a result, the belt type continuously variable transmission 110 may not be able to sufficiently suppress the fuel consumption of the internal combustion engine 120.

  As described above, in the belt-type continuously variable transmission 110 including the hydraulic oil confining device, in order to suppress an increase in fuel consumption of the internal combustion engine 120, the primary pulley hydraulic chamber 54 is closed and opened. The timing of switching is an important factor. Therefore, in the belt type continuously variable transmission 110 of the present embodiment, when the primary pulley hydraulic chamber 54 is next closed after the primary pulley hydraulic chamber 54 is opened, the primary pulley hydraulic chamber 54 is Is kept closed at an optimal time, thereby suppressing an increase in fuel consumption of the internal combustion engine 120.

  The belt type continuously variable transmission 110 has the following configuration and control procedure. The belt type continuously variable transmission 110 includes a hydraulic oil flow sensor D02 shown in FIG. 2, a hydraulic oil temperature sensor D01 shown in FIG. 1, a transmission ratio sensor D03, and a transmission control device 20 configured to be incorporated in the ECU 40. With.

  The hydraulic fluid flow sensor D02 shown in FIG. 2 is provided in the first oil passage OL01 between the gear ratio control side regulator ORa and the primary pulley hydraulic chamber 54. The hydraulic fluid flow sensor D02 detects the flow rate of the hydraulic fluid guided to the primary pulley hydraulic chamber 54. The hydraulic oil flow sensor D02 is electrically connected to the ECU 40. As a result, the ECU 40 acquires the flow rate of the hydraulic fluid guided from the hydraulic fluid flow rate sensor D02 to the primary pulley hydraulic chamber 54.

  The hydraulic oil temperature sensor D01 shown in FIG. 1 is provided in an oil pan in which the hydraulic oil of the belt type continuously variable transmission 110 is stored, and detects the temperature of the hydraulic oil in the oil pan. The hydraulic oil temperature sensor D01 is electrically connected to the ECU 40. Thereby, ECU40 acquires the temperature of the hydraulic fluid in belt type continuously variable transmission 110 from hydraulic fluid temperature sensor D01.

  The speed ratio sensor D03 includes an input side rotational speed sensor D03a and an output side rotational speed sensor D03b. The input side rotational speed sensor D03a is provided on the primary shaft 51 and detects the rotational speed of the primary shaft 51. The output side rotational speed sensor D03b is provided on the secondary shaft 61 and detects the rotational speed of the secondary shaft 61. The input side rotational speed sensor D03a and the output side rotational speed sensor D03b are electrically connected to the ECU 40. Thereby, ECU40 acquires the present gear ratio of belt type continuously variable transmission 110 from gear ratio sensor D03.

  FIG. 5 is a conceptual diagram showing the configuration of the transmission control apparatus according to the present embodiment. The ECU 40 is electrically connected to the internal combustion engine 120 shown in FIG. 1, the speed ratio control side regulator ORa, the close control side regulator ORb, etc. shown in FIG. 2, and the internal combustion engine 120, the speed ratio control side regulator ORa, Controls the operation of the control target such as the control side regulator ORb.

  The ECU 40 is also electrically connected to, for example, an injector of the internal combustion engine 120, a spark plug, an actuator for adjusting the opening of the electronic throttle valve, and the like. Thereby, the ECU 40 controls the fuel injection amount and fuel injection timing of the injector, the ignition timing of the spark plug, the opening degree of the electronic throttle valve, and the like. That is, the ECU 40 controls the torque extracted from the internal combustion engine 120 by controlling the injector, spark plug, electronic throttle valve, and the like.

  The ECU 40 also detects each of the detection means of the internal combustion engine 120, such as the hydraulic oil temperature sensor D01, the input side rotational speed sensor D03a, the output side rotational speed sensor D03b, the hydraulic fluid flow sensor D02 shown in FIG. To obtain various information from these detection means.

  As shown in FIG. 5, the transmission control device 20 is configured to be incorporated in a central processing unit Ep of the ECU 40. The ECU 40 includes a central processing unit Ep, a storage unit Em, an input port INp and an output port OUTp, an input interface IFin, and an output interface IFout. Note that the transmission control device 20 may be prepared separately from the ECU 40 and connected to the ECU 40.

  The transmission control device 20 includes an information acquisition unit 21, a comparison determination unit 22, a calculation unit 23, a transmission ratio control unit 24, and a closing control unit 25. The information acquisition unit 21 will be described later as a result of detection by detection means such as the hydraulic oil flow sensor D02 shown in FIG. 2, the hydraulic oil temperature sensor D01, the input side rotational speed sensor D03a, and the output side rotational speed sensor D03b shown in FIG. Information stored in the storage unit Em, information held by the engine control unit 26, and the like are acquired.

  The comparison determination unit 22 compares the numerical values obtained by the information acquisition unit 21 from each detection unit and the numerical values acquired from the storage unit Em. The calculation unit 23 performs a calculation on the numerical value acquired by the information acquisition unit 21. For example, the calculation unit 23 performs a calculation such as addition on a counter included in the central processing unit Ep.

  The gear ratio control unit 24 controls the gear ratio of the belt-type continuously variable transmission 110 so that the rotation speed of the primary shaft 51 becomes a target rotation speed. The closing control unit 25 controls the operation of the hydraulic oil closing device 10 shown in FIG.

  The central processing unit Ep includes an engine control unit 26 in addition to the transmission control device 20. The engine control unit 26 performs operation control of the internal combustion engine 120. Central processing unit Ep and storage unit Em are connected by a bus Bc. The central processing unit Ep and the input port INp are connected by a bus Ba. Central processing unit Ep and output port OUTp are connected by bus Bb.

  The information acquisition unit 21 of the transmission control device 20 acquires operation control data of the internal combustion engine 120 included in the engine control unit 26 and uses this. Further, the transmission control device 20 may interrupt a procedure for controlling the transmission ratio of the belt-type continuously variable transmission 110 in an operation control routine of the internal combustion engine 120 provided in advance in the engine control unit 26.

  An input interface IFin is connected to the input port INp. Connected to the input interface IFin are the hydraulic oil temperature sensor D01, the input side rotational speed sensor D03a, the output side rotational speed sensor D03b, the hydraulic oil flow sensor D02 shown in FIG. 2, and various other detection means.

  Signals output from these various detection means are converted into signals that can be used by the central processing unit Ep by the analog / digital converter ADC and the digital input buffer DIB in the input interface IFin and sent to the input port INp. Thereby, the central processing unit Ep can acquire information necessary for control of the transmission ratio of the belt type continuously variable transmission 110 and control of the internal combustion engine 120.

  An output interface IFout is connected to the output port OUTp. A gear ratio control side regulator ORa and a closing control side regulator ORb are connected to the output interface IFout. The output interface IFout is connected to an injector of the internal combustion engine 120, a spark plug, an electronic throttle valve actuator, and other control targets in the internal combustion engine 120.

  The output interface IFout includes a control circuit IFouta, a control circuit IFoutb, a control circuit IFoutc, and the like, and operates the control target based on a control signal calculated by the central processing unit Ep. With such a configuration, based on the output signal from the detection means, the central processing unit Ep of the ECU 40 controls the transmission ratio control side regulator ORa, the closing control side regulator ORb, the injector, the spark plug, and the electronic throttle valve. The transmission ratio of the belt type continuously variable transmission 110 and the output of the internal combustion engine 120 are controlled.

  The storage unit Em stores a computer program including a procedure for controlling the gear ratio of the belt type continuously variable transmission 110 and a control data map. The storage unit Em can be configured by a volatile memory such as a RAM (Random Access Memory), a nonvolatile memory such as a flash memory, or a combination thereof.

  The computer program may be capable of realizing a procedure for controlling the gear ratio of the belt type continuously variable transmission 110 by a combination with a computer program already recorded in the central processing unit Ep. Moreover, this transmission control apparatus 20 may implement | achieve an equivalent function using a dedicated hardware instead of the said computer program.

  FIG. 6 is a flowchart showing a procedure for controlling the hydraulic oil confining device of the belt type continuously variable transmission according to the present embodiment. The procedure shown below is a procedure for determining whether or not the primary pulley hydraulic chamber 54 is again closed after the primary pulley hydraulic chamber 54 is switched from the closed state to the open state.

  In step ST101, the information acquisition unit 21 acquires opening / closing information, which is information indicating whether the primary pulley hydraulic chamber 54 is in a closed state or an open state, from the storage unit Em. Next, in step ST102, the comparison determination unit 22 determines whether or not the primary pulley hydraulic chamber 54 is in an open state based on the opening / closing information acquired by the information acquisition unit 21 in step ST101.

  When the opening / closing information is not stored in the storage unit Em, the comparison / determination unit 22 determines whether the primary pulley hydraulic chamber 54 is based on the flow rate of the hydraulic fluid guided to the primary pulley hydraulic chamber 54 detected by the hydraulic fluid flow sensor D02. You may determine whether it is an open state. For example, when the flow rate of the hydraulic fluid guided to the primary pulley hydraulic chamber 54 is 0, the comparison determination unit 22 determines that the primary pulley hydraulic chamber 54 is in a closed state.

  When the opening / closing information is not stored in the storage unit Em, the comparison / determination unit 22 determines whether or not the primary pulley hydraulic chamber 54 is in an open state based on a change in the transmission ratio acquired by the transmission ratio sensor D03. May be. For example, when there is no change in the gear ratio, that is, when the gear ratio is fixed, the comparison determination unit 22 determines that the primary pulley hydraulic chamber 54 is in a closed state.

  However, even if the gear ratio is fixed, the primary pulley hydraulic chamber 54 is not necessarily closed. Therefore, the comparison / determination unit 22 determines whether or not the primary pulley hydraulic chamber 54 is in an open state based on both the flow rate of hydraulic oil guided to the primary pulley hydraulic chamber 54 and the change in the gear ratio. Therefore, the open / close state of the primary pulley hydraulic chamber 54 can be determined more accurately.

  Even if one of the detection means of the hydraulic oil flow sensor D02 and the gear ratio sensor D03 has a problem, the comparison determination unit 22 is based on the detection result detected by the other detection means. It can be determined whether or not the primary pulley hydraulic chamber 54 is open.

  When the primary pulley hydraulic chamber 54 is in a closed state (No in step ST102), the transmission control device 20 repeatedly executes the contents of step ST101 and the contents of step ST102 until the primary pulley hydraulic chamber 54 is opened. To do.

  In step ST102, when the primary pulley hydraulic chamber 54 is in the open state (step ST102, Yes), in step ST103, the comparison determination unit 22 switches the current open state of the primary pulley hydraulic chamber 54 from the closed state. It is determined whether it is immediately after.

  When the current open state of the primary pulley hydraulic chamber 54 is immediately after switching from the closed state (step ST103, Yes), the calculation unit 23 starts counting up the count CT from 0 in step ST104. Here, the count CT is the time elapsed from the starting point when the primary pulley hydraulic chamber 54 is switched from the closed state to the open state. In step ST104, the calculation unit 23 starts counting up the hydraulic oil flow rate Qo, which is the flow rate of the hydraulic oil guided to the primary pulley hydraulic chamber 54, from zero.

  When the current open state of the primary pulley hydraulic chamber 54 is not immediately after switching from the closed state, that is, when the current open state of the primary pulley hydraulic chamber 54 is due to the maintenance of the open state of the primary pulley hydraulic chamber 54 ( In step ST103, No), in step ST105, the calculation unit 23 updates the current count CT. The count CT updated by the calculation unit 23 is stored in the storage unit Em.

  In step ST105, the calculation unit 23 updates the hydraulic oil flow rate Qo from the starting point when the primary pulley hydraulic chamber 54 is switched from the closed state to the open state. Specifically, the calculation unit 23 sequentially adds the current hydraulic fluid flow rate acquired by the information acquisition unit 21 from the hydraulic fluid flow sensor D02 after the primary pulley hydraulic chamber 54 is switched from the closed state to the open state. By doing so, the hydraulic oil flow rate Qo is calculated. The hydraulic oil flow rate Qo updated by the calculation unit 23 is stored in the storage unit Em.

  When the content of step ST103 or the content of step ST104 is executed by the calculation unit 23, then in step ST106, the comparison determination unit 22 causes the closing control unit 25 to move the primary pulley to the belt type continuously variable transmission 110. The closing request information, which is information as to whether or not the hydraulic chamber 54 is to be closed, is acquired from the storage unit Em.

  Here, the closing request information is determined whether or not the primary pulley hydraulic chamber 54 should be closed by a closing determination procedure which is a procedure different from the procedure shown in FIG. 6, and is stored in the storage unit Em. ing. Here, an example of the closing determination procedure will be described below.

  The comparison / determination unit 22 sets the primary pulley hydraulic chamber 54 based on the gear ratio of the belt type continuously variable transmission 110, the vehicle speed of the vehicle 100, the torque extracted from the internal combustion engine 120, the driving force of the vehicle 100, and the like. It is determined whether or not it should be closed.

  Next, in step ST107, the comparison determination unit 22 has a closing request that is a request to bring the primary pulley hydraulic chamber 54 into a closed state based on the closing request information acquired by the information acquisition unit 21 in step ST106. It is determined whether or not. When there is no closing request, that is, when the comparison determination unit 22 determines that the primary pulley hydraulic chamber 54 should not be closed (No at Step ST107), there is a closing request (Step ST107, Yes). ) Until the transmission control device 20 repeatedly executes the contents from step ST101 to step ST107.

  If it is determined in step ST107 that there is a closing request (step ST107, Yes), in step ST108, the information acquisition unit 21 acquires the current count CT from the storage unit Em. Next, in step ST109, the comparison determination unit 22 determines whether or not the count CT is equal to or greater than a predetermined value a.

  Here, the predetermined value a is a time during which it is considered that the temperature of the hydraulic oil of the belt type continuously variable transmission 110 has decreased to the environmental temperature. Here, the environmental temperature is a temperature of hydraulic oil in a general oil pan in which the belt-type continuously variable transmission 110 is operating, and is in a range in which the operation of the belt-type continuously variable transmission 110 does not cause inconvenience. Temperature. The environmental temperature is, for example, 80 degrees to 120 degrees.

  As described above, the temperature of the hydraulic oil in the primary pulley hydraulic chamber 54 rises while the primary pulley hydraulic chamber 54 is closed. Therefore, when the temperature of the hydraulic oil in the primary pulley hydraulic chamber 54 exceeds an appropriate temperature, the primary pulley hydraulic chamber 54 is opened by the closing control unit 25.

  As a result, the hydraulic oil in the primary pulley hydraulic chamber 54 is discharged from the primary pulley hydraulic chamber 54 and returned to the oil pan of the belt type continuously variable transmission 110. As a result, the temperature of the hydraulic oil in the primary pulley hydraulic chamber 54 is lower than when the primary pulley hydraulic chamber 54 is in a closed state.

  However, when the primary pulley hydraulic chamber 54 is in the closed state, the hydraulic oil that has received heat in the primary pulley hydraulic chamber 54 and has risen in temperature mixes with the hydraulic oil in the oil pan. Temperature rises. Hereinafter, the temperature of the hydraulic oil in the oil pan is referred to as the hydraulic oil temperature To as the temperature of the hydraulic oil in the belt type continuously variable transmission 110 as a whole.

  Therefore, if the primary pulley hydraulic chamber 54 is switched from the closed state to the open state and the primary pulley hydraulic chamber 54 is brought into the closed state without a sufficient interval just because there is a request for closing, the hydraulic oil is discharged. Is guided again into the primary pulley hydraulic chamber 54 in a state where the temperature has not sufficiently decreased.

  Therefore, when the primary pulley hydraulic chamber 54 is switched from the closed state to the open state and the primary pulley hydraulic chamber 54 is closed without a sufficient interval, the temperature of the hydraulic oil in the primary pulley hydraulic chamber 54 is increased. Time to exceed the proper temperature is reduced.

  The appropriate temperature refers to the actual gear ratio generated when the hydraulic oil temperature rises in the primary pulley hydraulic chamber 54 and the hydraulic oil expands, and the gear ratio targeted by the belt-type continuously variable transmission 110. Due to this difference, the increase in the amount of fuel consumed by the internal combustion engine 120 when the vehicle 100 travels is a value that does not cause a problem. The predetermined value a is, for example, a value between 80 degrees and 120 degrees.

  Here, even when there is a closing request for the belt type continuously variable transmission 110, the primary pulley hydraulic chamber 54 is closed without sufficient interval since the primary pulley hydraulic chamber 54 is switched from the closed state to the open state. When this occurs, switching between the closed state and the open state of the primary pulley hydraulic chamber 54 frequently occurs.

  Therefore, in this embodiment, when there is a closing request, the transmission control device 20 switches the primary pulley hydraulic chamber 54 from the closed state to the opened state, and a predetermined value a that is a predetermined time has elapsed. After that, the primary pulley hydraulic chamber 54 is closed.

  That is, the transmission control device 20 reduces the temperature of the hydraulic oil in the primary pulley hydraulic chamber 54 from the starting point based on the time that has elapsed since the primary pulley hydraulic chamber 54 was switched from the closed state to the open state. Estimate the amount.

  Here, the longer the elapsed time since the primary pulley hydraulic chamber 54 is switched from the closed state to the open state, the more hydraulic oil is discharged from the primary pulley hydraulic chamber 54, and more new hydraulic oil is discharged from the primary pulley. The pulley is guided into the pulley hydraulic chamber 54. Therefore, the amount of decrease in the temperature of the hydraulic oil in the primary pulley hydraulic chamber 54 increases as the time elapsed after the primary pulley hydraulic chamber 54 is switched from the closed state to the open state becomes longer.

  The time elapsed after the primary pulley hydraulic chamber 54 is switched from the closed state to the open state and the amount of decrease in the temperature of the hydraulic oil in the primary pulley hydraulic chamber 54 are in the relationship described above. Therefore, the transmission control device 20 has this relationship as a map or an arithmetic expression, and the time elapsed since the primary pulley hydraulic chamber 54 was switched from the closed state to the open state using the map or the arithmetic expression. From this, the amount of decrease in the temperature of the hydraulic oil in the primary pulley hydraulic chamber 54 is estimated.

  The transmission control device 20 permits switching of the primary pulley hydraulic chamber 54 from the open state to the closed state when the estimated amount of decrease in the temperature of the hydraulic oil in the primary pulley hydraulic chamber 54 is sufficient. To do.

  As described above, the predetermined value a is a time in a range where the temperature of the hydraulic oil of the belt type continuously variable transmission 110 is considered to have decreased to the environmental temperature, and as a result, the primary pulley hydraulic chamber 54 is opened. The time is within a range in which frequent switching between the state and the closed state can be suppressed.

  That is, the transmission control device 20 compares the count CT with the predetermined value “a” in step ST109 in order to prevent frequent switching between the open state and the closed state of the primary pulley hydraulic chamber 54. Thus, it is determined whether or not the amount of decrease in the temperature of the hydraulic oil in the primary pulley hydraulic chamber 54 is sufficient.

  If it is determined that the count CT is smaller than the predetermined value a (step ST109, No), the transmission control device 20 performs the step until it is determined that the count CT is equal to or greater than the predetermined value a (step ST109, Yes). The contents from ST101 to step ST109 are repeatedly executed.

  When it is determined that the count CT is greater than or equal to the predetermined value a (step ST109, Yes), in step ST110, the information acquisition unit 21 acquires the current hydraulic oil temperature To from the hydraulic oil temperature sensor D01. Next, in step ST111, the comparison determination unit 22 determines whether or not the hydraulic oil temperature To is equal to or less than a predetermined value b.

  Here, the predetermined value b is the environmental temperature described above. That is, the predetermined value b is a temperature at which a decrease in time until the temperature of the hydraulic oil in the primary pulley hydraulic chamber 54 exceeds an appropriate temperature can be suppressed. The transmission control device 20 compares the hydraulic oil temperature To with the predetermined value b in step ST111 in order to prevent frequent switching between the open state and the closed state of the primary pulley hydraulic chamber 54. Thus, it is determined whether or not the amount of decrease in the temperature of the hydraulic oil in the primary pulley hydraulic chamber 54 is sufficient.

  That is, the transmission control device 20 estimates the amount of decrease in the temperature of the hydraulic oil in the primary pulley hydraulic chamber 54 based on the hydraulic oil temperature To that is the current temperature of the hydraulic oil in the oil pan. Here, as the hydraulic oil temperature To, which is the current temperature of the hydraulic oil in the oil pan, is lower, new hydraulic oil having a lower temperature in the primary pulley hydraulic chamber 54 is supplied from the oil pan. Accordingly, the lower the hydraulic oil temperature To, which is the current temperature of the hydraulic oil in the oil pan, the greater the amount of decrease in the temperature of the hydraulic oil in the primary pulley hydraulic chamber 54.

  The hydraulic oil temperature To, which is the current temperature of the hydraulic oil in the oil pan, and the amount of decrease in the hydraulic oil temperature in the primary pulley hydraulic chamber 54 are in the relationship described above. Therefore, the transmission control device 20 has this relationship as a map or an arithmetic expression, and the primary pulley hydraulic pressure is calculated from the hydraulic oil temperature To, which is the current temperature of the hydraulic oil in the oil pan, using the map or the arithmetic expression. The amount of decrease in the temperature of the hydraulic oil in the chamber 54 is estimated.

  Note that the change in temperature of the hydraulic oil in the oil pan is smaller than that of the hydraulic oil in the primary pulley hydraulic chamber 54. This is because the hydraulic oil in the oil pan has a larger heat capacity because the hydraulic oil in the oil pan is larger than the hydraulic oil in the primary pulley hydraulic chamber 54. Therefore, the hydraulic oil temperature To may not be exactly the temperature at the starting point. The hydraulic oil temperature To may be a temperature approximate to the temperature at the starting point, even if the temperature is around the starting point.

  The transmission control device 20 closes the primary pulley hydraulic chamber 54 from the open state when the estimated amount of decrease in the temperature of the hydraulic oil in the primary pulley hydraulic chamber 54 is sufficient. Allow switching to the closed state.

  When it is determined that the hydraulic oil temperature To is greater than the predetermined value b (step ST111, No), the transmission control device until the hydraulic oil temperature To is determined to be equal to or lower than the predetermined value b (step ST111, Yes). In step 20, the contents from step ST101 to step ST111 are repeatedly executed.

  When it is determined that the hydraulic oil temperature To is equal to or lower than the predetermined value b (Yes in Step ST111), in Step ST112, the information acquisition unit 21 switches the primary pulley hydraulic chamber 54 from the closed state to the open state. The hydraulic oil flow rate Qo from the storage unit Em is acquired. Next, in step ST113, the comparison determination unit 22 determines whether or not the hydraulic oil flow rate Qo is equal to or greater than a predetermined value c.

  Here, when the primary pulley hydraulic chamber 54 is switched from the closed state to the open state, new hydraulic oil is introduced into the primary pulley hydraulic chamber 54. The temperature of the new hydraulic oil is lower than the temperature of the hydraulic oil confined in the primary pulley hydraulic chamber 54 while the primary pulley hydraulic chamber 54 is closed.

  Therefore, when the new hydraulic oil is introduced into the primary pulley hydraulic chamber 54, the new hydraulic oil and the hydraulic oil in the primary pulley hydraulic chamber 54 are mixed. As a result, the temperature of the hydraulic oil in the primary pulley hydraulic chamber 54 decreases. Thus, the temperature of the hydraulic oil in the primary pulley hydraulic chamber 54 decreases as the amount of the new hydraulic oil increases, compared to when the primary pulley hydraulic chamber 54 is in the closed state.

  The predetermined value c is a flow rate at which it can be determined that the new hydraulic oil is introduced into the primary pulley hydraulic chamber 54 at a temperature equal to or lower than an appropriate temperature by being guided by the predetermined value c or more. Note that, as described above, the appropriate temperature refers to the actual gear ratio generated when the hydraulic oil temperature rises in the primary pulley hydraulic chamber 54 and the hydraulic oil expands, and the belt-type continuously variable transmission 110 When the vehicle 100 travels due to the difference from the target gear ratio, the increase in the amount of fuel consumed by the internal combustion engine 120 is a temperature that does not cause a problem.

  The transmission control device 20 compares the hydraulic oil flow rate Qo with the predetermined value c in step ST113 in order to prevent frequent switching between the open state and the closed state of the primary pulley hydraulic chamber 54. Thus, it is determined whether or not the amount of decrease in the temperature of the hydraulic oil in the primary pulley hydraulic chamber 54 is sufficient.

  That is, the transmission control device 20 performs the primary control based on the hydraulic fluid flow Qo that is the flow rate of the hydraulic fluid guided to the primary pulley hydraulic chamber 54 after the primary pulley hydraulic chamber 54 is switched from the closed state to the open state. The amount of decrease in the temperature of the hydraulic oil in the pulley hydraulic chamber 54 is estimated.

  Here, the greater the hydraulic fluid flow Qo, which is the flow rate of hydraulic fluid guided to the primary pulley hydraulic chamber 54 after the primary pulley hydraulic chamber 54 is switched from the closed state to the open state, the more hydraulic fluid is primary. More new hydraulic fluid is discharged from the pulley hydraulic chamber 54 and guided into the primary pulley hydraulic chamber 54.

  Therefore, the operation in the primary pulley hydraulic chamber 54 increases as the hydraulic fluid flow Qo, which is the flow rate of the hydraulic fluid guided to the primary pulley hydraulic chamber 54 after the primary pulley hydraulic chamber 54 is switched from the closed state to the open state, is increased. The amount of decrease in oil temperature increases.

  The hydraulic oil flow rate Qo that is the flow rate of the hydraulic oil guided to the primary pulley hydraulic chamber 54 after the primary pulley hydraulic chamber 54 is switched from the closed state to the open state, and the temperature of the hydraulic oil in the primary pulley hydraulic chamber 54 The amount of decrease is in the above relationship. Therefore, the transmission control device 20 has this relationship as a map or an arithmetic expression, and the primary pulley hydraulic pressure after the primary pulley hydraulic chamber 54 is switched from the closed state to the open state using the map or the arithmetic expression. The amount of decrease in the temperature of the hydraulic oil in the primary pulley hydraulic chamber 54 is estimated from the hydraulic oil flow rate Qo that is the flow rate of the hydraulic oil guided to the chamber 54.

  The transmission control device 20 permits switching of the primary pulley hydraulic chamber 54 from the open state to the closed state when the estimated amount of decrease in the temperature of the hydraulic oil in the primary pulley hydraulic chamber 54 is sufficient. To do.

  If it is determined that the hydraulic oil flow rate Qo is smaller than the predetermined value c (step ST113, No), the transmission control device until the hydraulic oil flow rate Qo is determined to be greater than or equal to the predetermined value c (step ST113, Yes). In step 20, the contents from step ST101 to step ST113 are repeatedly executed.

  When it is determined that the hydraulic oil flow rate Qo is equal to or less than the predetermined value c (step ST113, Yes), in step ST114, the closing control unit 25 brings the primary pulley hydraulic chamber 54 into a closed state. Specifically, the closing control unit 25 controls the closing control side regulator ORb so that the product of the oil pressure Pcv and the pressure receiving area Ap adds the spring force Fsp to the product of the oil pressure Ps and the seal part area Acv. The hydraulic pressure Ps is adjusted so as to be less than or equal to the above value.

  Next, in step ST115, the calculation unit 23 resets the count CT and the hydraulic oil flow rate Qo stored in the storage unit Em. The transmission control device 20 repeatedly executes the contents of the above steps ST101 to ST115.

  Here, the contents of step ST108 and the contents of step ST109 are collectively referred to as step STA. Step STA is a determination procedure for preventing the primary pulley hydraulic chamber 54 from being closed until a predetermined time elapses after the primary pulley hydraulic chamber 54 is switched from the closed state to the open state.

  In step STA, the transmission control device 20 determines whether the temperature of the hydraulic oil in the belt-type continuously variable transmission 110 has decreased to the environmental temperature, and the temperature of the hydraulic oil in the primary pulley hydraulic chamber 54 is appropriate. Suppresses the decrease in time until the temperature is exceeded. As a result, the transmission control device 20 suppresses frequent switching between the open state and the closed state of the primary pulley hydraulic chamber 54 and suppresses an increase in fuel consumption of the internal combustion engine 120.

  Further, the transmission control device 20 frequently switches between the open state and the closed state of the primary pulley hydraulic chamber 54 regardless of the temperature of the hydraulic oil of the belt type continuously variable transmission 110 at step STA. It can also be suppressed. That is, as the value of the predetermined value a is increased, the time until the primary pulley hydraulic chamber 54 is switched from the open state to the closed state becomes longer. Accordingly, the transmission control device 20 can suppress frequent occurrence of switching between the open state and the closed state of the primary pulley hydraulic chamber 54.

  Also, the contents of step ST110 and the contents of step ST111 are collectively referred to as step STB. Step STB is a determination procedure for preventing the primary pulley hydraulic chamber 54 from being closed until the hydraulic oil temperature To of the current belt type continuously variable transmission 110 is lowered to an environmental temperature that is a predetermined temperature. is there.

  In step STB, the transmission control device 20 determines whether the hydraulic oil temperature To of the belt-type continuously variable transmission 110 has decreased to the environmental temperature, and the hydraulic oil temperature in the primary pulley hydraulic chamber 54 is appropriate. Suppresses the decrease in time until the temperature is exceeded. As a result, the transmission control device 20 suppresses frequent switching between the open state and the closed state of the primary pulley hydraulic chamber 54 and suppresses an increase in fuel consumption of the internal combustion engine 120.

  Further, the contents of step ST112 and the contents of step ST113 are collectively referred to as step STC. In step STC, after the primary pulley hydraulic chamber 54 is switched from the closed state to the open state, the primary pulley hydraulic chamber 54 is closed until a predetermined flow rate of hydraulic oil is guided to the primary pulley hydraulic chamber 54. This is a determination procedure for not.

  In step STC, the transmission control device 20 determines whether the temperature of the hydraulic oil in the primary pulley hydraulic chamber 54 has decreased to an appropriate temperature, and the temperature of the hydraulic oil in the primary pulley hydraulic chamber 54 is an appropriate temperature. Suppresses the decrease in time taken to exceed As a result, the transmission control device 20 suppresses frequent switching between the open state and the closed state of the primary pulley hydraulic chamber 54 and suppresses an increase in fuel consumption of the internal combustion engine 120.

  As described above, the transmission control device 20 executes all the procedures of step STA, step STB, and step STC. As a result, the transmission control device 20 more reliably suppresses frequent switching between the open state and the closed state of the primary pulley hydraulic chamber 54 and increases the fuel consumption of the internal combustion engine 120. Suppress. However, the present embodiment is not limited to this, and the transmission control device 20 may perform at least one of the steps STA, STB, and STC.

  In this case, since the number of procedures to be executed in the transmission control device 20 is reduced, the load when the transmission control device 20 executes the procedure for controlling the hydraulic oil confining device 10 is reduced. Further, the transmission control device 20 can suppress a decrease in time until the temperature of the hydraulic oil in the primary pulley hydraulic chamber 54 exceeds an appropriate temperature. As a result, the transmission control device 20 can suppress the occurrence of frequent switching between the open state and the closed state of the primary pulley hydraulic chamber 54 and suppress an increase in fuel consumption of the internal combustion engine 120.

  Further, the transmission control device 20 is closed in step ST114 when a positive determination is made in all of step STA (step ST109), step STB (step ST111), and step STC (step ST113). Although the insertion control unit 25 closes the primary pulley hydraulic chamber 54, the present embodiment is not limited to this. Below, the other procedure which controls the hydraulic oil confinement apparatus 10 is demonstrated as an example.

  FIG. 7 is a flowchart showing another procedure for controlling the hydraulic oil confining device of the belt type continuously variable transmission according to the present embodiment. Each procedure from step ST101 to step ST115 shown in FIG. 7 is the same as each procedure from step ST101 to step ST115 shown in FIG. Therefore, detailed description of each procedure is omitted, and the order executed by the transmission control device 20 will be mainly described.

  If the comparison determination unit 22 determines in step ST109 that a predetermined time has elapsed since the primary pulley hydraulic chamber 54 has been switched from the closed state to the open state (Yes in step ST109), the transmission control device 20 Moves to step ST114. When the comparison determination unit 22 determines in step ST109 that the predetermined time has not elapsed since the primary pulley hydraulic chamber 54 was switched from the closed state to the open state (No in step ST109), the transmission control device 20 Moves to step STB.

  If the comparison / determination unit 22 determines in step ST111 that the hydraulic oil temperature To has decreased to the ambient temperature (step ST111, Yes), the transmission control device 20 proceeds to step ST114. If the comparison / determination unit 22 determines in step ST111 that the hydraulic oil temperature To has not decreased to the environmental temperature (No in step ST111), the transmission control device 20 proceeds to step STC.

  In step ST <b> 113, when the comparison determination unit 22 introduces a sufficient amount of hydraulic oil into the primary pulley hydraulic chamber 54 so that the temperature of the hydraulic oil in the primary pulley hydraulic chamber 54 falls to an appropriate temperature. If it determines (step ST113, Yes), the transmission control apparatus 20 will transfer to step ST114. In step ST <b> 113, if the comparison / determination unit 22 does not introduce a sufficient amount of hydraulic oil into the primary pulley hydraulic chamber 54 to reduce the temperature of the hydraulic oil in the primary pulley hydraulic chamber 54 to an appropriate temperature. If determined (No in Step ST113), the transmission control device 20 repeatedly executes Step ST101 to Step ST113 until a positive determination is made in any of Step ST109, Step ST111, and Step ST113.

  As described above, the transmission control device 20 controls the transmission control even if the primary pulley hydraulic chamber 54 is in the closed state when a positive determination is made in any of step ST109, step ST111, and step ST113. The device 20 can suppress a decrease in time until the temperature of the hydraulic oil in the primary pulley hydraulic chamber 54 exceeds an appropriate temperature. As a result, the transmission control device 20 can suppress the occurrence of frequent switching between the open state and the closed state of the primary pulley hydraulic chamber 54 and suppress an increase in fuel consumption of the internal combustion engine 120.

  Note that the combination of step STA, step STB, and step STC is not limited to the above configuration, and may be any combination. For example, the transmission control device 20 may set a combination of step STA, step STB, and step STC based on the importance of step STA, step STB, and step STC. In this case, the transmission control device 20 can more reliably suppress a decrease in time until the temperature of the hydraulic oil in the primary pulley hydraulic chamber 54 exceeds an appropriate temperature. As a result, the transmission control device 20 suppresses frequent occurrence of switching between the open state and the closed state of the primary pulley hydraulic chamber 54, and more reliably increases the fuel consumption of the internal combustion engine 120. Can be suppressed.

  As described above, the belt-type continuously variable transmission according to the present invention is suitable for a belt-type continuously variable transmission including a hydraulic oil confining device and a transmission control device that controls the belt-type continuously variable transmission, It is suitable for suppressing an increase in fuel consumption of an internal combustion engine.

It is a mimetic diagram showing the whole composition in the power transmission portion of vehicles provided with the belt type continuously variable transmission concerning this embodiment. It is sectional drawing which shows the primary pulley which concerns on this embodiment. It is sectional drawing which expands and shows the hydraulic oil confinement apparatus in a primary pulley hydraulic chamber being closed. It is sectional drawing which expands and shows the hydraulic-oil confinement apparatus in a primary pulley hydraulic chamber being an open state. It is a conceptual diagram which shows the structure of the transmission control apparatus which concerns on this embodiment. It is a flowchart which shows the procedure which controls the hydraulic fluid confinement apparatus of the belt-type continuously variable transmission which concerns on this embodiment. It is a flowchart which shows the other procedure which controls the hydraulic fluid confinement apparatus of the belt-type continuously variable transmission which concerns on this embodiment.

Explanation of symbols

DESCRIPTION OF SYMBOLS 10 Hydraulic oil confinement apparatus 11 Piston operation | movement hydraulic chamber 12 Seal part 12a Tapered surface 12b Opening 13 Valve body 14 Piston 14a Pressure receiving surface 14b Rod-shaped part 15 Spring 20 Transmission control apparatus 21 Information acquisition part 22 Comparison determination part 23 Calculation part 24 Gear ratio control unit 25 Enclose control unit 26 Engine control unit 40 ECU
50 Primary pulley 51 Primary shaft 52 Primary fixed sheave 53 Primary movable sheave 54 Primary pulley hydraulic chamber 55 Spline 56 Primary partition wall 60 Secondary pulley 61 Secondary shaft 62 Secondary fixed sheave 63 Secondary movable sheave 80 Belt 80a Primary groove 80b Secondary groove 81-84 Bearing DESCRIPTION OF SYMBOLS 100 Vehicle 110 Belt type continuously variable transmission 120 Internal combustion engine 121 Crankshaft 130 Torque converter 131 Input shaft 140 Forward / reverse switching mechanism 150 Reduction gear 151 Final drive pinion 160 Differential gear 161 Ring gear 170 Drive shaft 180 Wheel D01 Hydraulic oil temperature sensor D02 Hydraulic oil flow sensor D03 Gear ratio sensor ADC Analog / Digital Converter Ba, Bb, Bc bus DIB digital input buffer Em storage unit Ep central processing unit IFin input interface IFout output interface IFouta to IFoutc control circuit INp input port OL01 first oil passage OL01a axial oil passage OL01b radial oil passage OL02 first Two oil passages OL02a Axial oil passage OL02b Radial oil passage OP Oil pump ORa Gear ratio control side regulator ORb Closed control side regulator OT Oil tank OUTp Output port RL Rotating shafts a, b, c Predetermined value Acv Seal part area Ap Pressure receiving Area CT count Fsp Spring force Pcv Hydraulic pressure Ps Hydraulic pressure Qo Hydraulic oil flow rate To Hydraulic oil temperature

Claims (6)

A shaft that receives the rotation extracted from the internal combustion engine and rotates about the rotation axis;
A fixed sheave coupled to the shaft and rotating about the rotation axis;
A movable sheave provided on the shaft so as to face the fixed sheave and moving on the shaft in the rotational axis direction;
A pulley hydraulic chamber that is provided on the shaft and applies a force in the direction of the rotation axis by the pressure of hydraulic oil to the movable sheave;
The amount of decrease in the temperature of the hydraulic oil in the pulley hydraulic chamber is switched from a state where discharge of the hydraulic oil in the pulley hydraulic chamber is prohibited to a state where discharge of the hydraulic oil in the pulley hydraulic chamber is permitted. Hydraulic oil confining means for prohibiting switching to a state in which discharge of the hydraulic oil from the pulley hydraulic chamber is prohibited based on the amount of decrease in the temperature of the hydraulic oil starting from
A belt type continuously variable transmission.   2. The belt-type continuously variable sensor according to claim 1, wherein the hydraulic oil confining means estimates a decrease in the temperature of the hydraulic oil from the starting point based on a time elapsed from the starting point. transmission.   The hydraulic oil confining means estimates the amount of decrease in the temperature of the hydraulic oil from the starting point based on the flow rate of the hydraulic oil guided to the pulley hydraulic chamber after the starting point. The belt-type continuously variable transmission according to claim 1.   The said hydraulic oil confinement means estimates the amount of decrease in the temperature of the hydraulic oil from the starting point based on the temperature of the hydraulic oil guided to the pulley hydraulic chamber. Belt type continuously variable transmission.   The hydraulic oil confining means is configured to reduce the amount of hydraulic oil temperature estimated based on the elapsed time from the calculation point and the flow rate of hydraulic oil introduced to the pulley hydraulic chamber after the calculation point. The amount of decrease in the temperature of the hydraulic oil estimated based on the amount of decrease in the temperature of the hydraulic oil estimated based on the flow rate of the hydraulic oil guided to the pulley hydraulic chamber after the starting point The belt-type continuously variable transmission according to claim 1, wherein switching to a state in which discharge of the hydraulic oil from the pulley hydraulic chamber is prohibited is prohibited.   A shaft that rotates with the rotation taken out from the internal combustion engine as an axis, rotates around the rotation shaft, a fixed sheave connected to the shaft and rotates about the rotation shaft, and a shaft facing the fixed sheave. And a movable sheave that moves on the shaft in the direction of the rotation axis, and a pulley hydraulic chamber that is provided on the shaft and applies a force in the direction of the rotation axis to the movable sheave by the pressure of hydraulic oil. A transmission control device for controlling a continuously variable transmission, wherein the hydraulic oil temperature in the pulley hydraulic chamber is reduced, and the hydraulic oil in the pulley hydraulic chamber is prohibited from being discharged. Based on the amount of decrease in the temperature of the hydraulic oil starting from the time when the hydraulic oil is allowed to be discharged into the pulley hydraulic chamber, Transmission control apparatus, characterized in that the discharge of the hydraulic oil to prohibit switching to the condition to be inhibited.

Images