Control apparatus for hydraulic servo units

Abstract: A hydraulic servo unit (50) comprises a cylinder (51) and a piston (54) slidably inserted therein, the cylinder chamber being divided by a piston portion into a rod-side cylinder chamber (53) and a head-side cylinder chamber (52). A control apparatus for the hydraulic servo unit comprises a first hydraulic line (101, 102) connecting the rod-side cylinder chamber with the hydraulic pressure source which supplies working fluid of predetermined pressure, a second hydraulic line (103,104) connecting the head-side cylinder chamber with the first hydraulic line through a first solenoid valve (151) of duty-ratio-control, and a drain hydraulic line (106) connecting the head-side cylinder chamber with drain through a second solenoid valve (152) of duty-ratio-control.

Description: The invention relates to a control apparatus that utilizes solenoid valves for controlling hydraulic servo units which are used, for example, for speed reduction ratio control and clutch control required in a variable speed transmission. There have been proposed various types of continuously variable speed transmissions for vehicles used in continuously varying the input rotational speed and transmitting it as an output. For example, Japanese Patent Laid-Open Publication No.56(1981)-95722 discloses a continuously variable speed transmission for vehicles, comprising a closed hydraulic circuit having therein a constant displacement hydraulic pump and a variable displacement hydraulic motor. In such a continuously variable speed transmission, clutch operation at the time of starting or stopping and speed reduction ratio change during cruising are controlled by servo units based on signals representing the engine throttle opening and the vehicle speed. For example, such control may be given as shown in FIG. 7A, by means of four solenoid valves 163a through 163d which serves to increase or decrease the hydraulic pressure Pl of the working fluid supplied from the line 162 connected with the right and left cylinders of the servo cylinder 161, or as shown in FIG. 7B, by means of two solenoid valves 166a and 166b which function via a four-way valve 165. In the case of FIG. 7A, however, as many as four solenoid valves are needed, and in the case of FIG. 7B a four-way valve is needed, though four valves are not required. In any case the use of these valves makes the constitution and the control of the servo unit not only complicated but also costly. In particular, in a continuously variable speed transmission this leads to a disadvantage that the transmission becomes large in size and complex since it requires servo units for controlling speed reduction ratio and clutch operation, respectively. There has been known another disadvantage with a conventional servo unit that it cannot provide desirable control in the case of solenoid valve malfunction. Therefore, various constitutions for such servo units have been disclosed in prior arts as a fail-safe measure in the event of such solenoid valve malfunction, in which, for example, one of the servo units is slowly operated by slowly releasing the clutch off. For example, Japanese Patent Laid-Open Publication No.60(1985)-249761, discloses an apparatus in which a four-way valve undertakes pressure control in the right and left cylinder chambers of the servo cylinder for ratio control of a continuously variable speed transmission. The operation of the four-way valve being controlled by a solenoid valve and, in case the solenoid valve is inoperable due to its malfunction, the four-way valve is maintained so as to prohibit the ratio control, or the hydraulic fluid is furnished through an orifice so as to slowly vary the reduction ratio until the ratio reaches its maximum or minimum. However, if the reduction ratio is prohibited to change as illustrated above, it remains so and cannot be reduced to LOW (maximum speed reduction ratio) when the vehicle is started again, and hence a smooth start will not be available. Furthermore, the use of a four-way valve entails above mentioned disadvantage that the control apparatus becomes large in size and complex. Clutch control for a transmission is, as mentioned above, often given by mean of servo units utilizing solenoid valves. With these systems it may happen that the solenoid valves fail to operate, leaving the clutch in operational engagement even if the shift lever is brought back to its neutral position and OFF signal is generated. An object of the invention is to provide a control apparatus which can control the operation of servo units by means of only two solenoid valves. An object of one embodiment is to provide a speed control apparatus which is simple in structure, easy to control, and not costly. A further object of such embodiment is to provide a reliable speed control apparatus capable of furnishing a fail-safe operation in case solenoids fail. An object of a further embodiment is to provide a control apparatus for use with servo units for controlling a clutch of a transmission, which is capable of switching the clutch from ON state to OFF state by bringing the shift lever into neutral position if the clutch is turned ON by solenoid valve malfunction. From EP-A-312357 published on 19/04/89 there is known a control apparatus for a hydraulic servo unit comprising a cylinder and a piston inserted in a chamber formed in said cylinder, said piston having a piston portion which is slidably inserted in said cylinder chamber and a rod portion with one end thereof being fast with said piston portion and the other end thereof extending out of said cylinder chamber, said cylinder chamber being divided by said piston portion into a rod-side cylinder chamber through which said piston rod penetrates and a head-side cylinder chamber to which the end surface of said piston portion faces, a pressure receiving area of said head-side cylinder chamber being greater than a pressure receiving area of said rod-side cylinder chamber; the control apparatus comprising: a first hydraulic line for supplying a working fluid of predetermined pressure from a hydraulic pressure source to said rod-side cylinder chamber; a first solenoid valve whose opening is controlled in accordance with duty ratio signals; a second hydraulic line connecting said head-side cylinder chamber with said first hydraulic line via said first solenoid valve; a second solenoid valve whose opening is controlled in accordance with duty ratio signals; a drain hydraulic line connecting said head-side cylinder chamber with a drain via said second solenoid valve; and wherein a first orifice having a flow passage area is provided in said second hydraulic line, and a second orifice having a flow passage area is provided in said drain hydraulic line. The control apparatus of the present invention as defined in claim 1 further comprises said first orifice having a predetermined fixed flow passage area provided in said second hydraulic line, and said second orifice having a predetermined fixed flow passage area smaller than said area of the first orifice provided in said drain hydraulic line. Alternative prior art control devices for hydraulic servo units are known from EP 0065304 and EP 0240178 which disclose various different arrangements of solenoids and hydraulic supply and drain lines for controlling fluid pressure to a servo unit. In one embodiment, the apparatus of the present invention further comprises a hydraulic branch line one end of which is connected with a portion of said second hydraulic line between said hydraulic pressure source and said first solenoid valve, and the other end of which is connected with said head-side cylinder chamber; a check valve provided in said hydraulic branch line for permitting the working fluid to flow only from said head-side cylinder chamber into said second hydraulic pressure line at a point by-passing the first solenoid valve, and not permitting the fluid to flow from said second hydraulic pressure line by-passing said first solenoid valve through said hydraulic branch line into said head-side cylinder; and a shift valve additionally provided in a portion of said second hydraulic line between said hydraulic pressure source and a branching point of said branch line; wherein said shift valve shuts the second hydraulic line on a side of said hydraulic pressure source and connects the second hydraulic line on a side of said branching point with a drain when a neutral range is selected, but allows working fluid to flow through said second hydraulic line by directly connecting the head-side cylinder chamber and the first hydraulic line via the first solenoid valve when a running range is selected. The present invention will become more fully understood from the detailed description given hereinbelow and the accompanying drawings which are given by way of illustration only, and thus are not limitative of the present invention and wherein: FIG. 1 is a schematic diagram of a hydraulic circuit used in a continuously variable speed transmission having a control apparatus according a further embodiment. FIG. 2 is a cross sectional view of a first and a second speed control servo unit. FIG. 3 is a cross sectional view of a clutch servo unit. FIG. 4 is a schematic diagram of a hydraulic circuit used in a continuously variable speed transmission having a control apparatus units according to a further embodiment. FIG. 5 is a cross sectional view of a directional control servo unit used in the above mentioned continuously variable speed transmission. FIG. 6 is a cross sectional view of a clutch servo unit for the above mentioned continuously variable speed transmission. FIGS. 7A and 7B are schematic diagrams of hydraulic circuit for servo units according to the prior arts. Fig.1 shows a hydraulic circuit diagram of a continuously variable speed transmission provided with a control apparatus, of a first embodiment according to the invention. The continuously variable speed transmission has a constant displacement hydraulic pump P driven by the engine E through the input shaft 1 and a variable displacement hydraulic motor M connected to the output shaft 2 driving the wheels W. These hydraulic pump P and motor M constitute a closed hydraulic circuit along with two hydraulic lines: the first hydraulic line La by which the delivery port of the pump P communicates with the suction port of the motor M, and the second hydraulic line Lb by which the suction port of the pump P does with the delivery port of the motor M. A charge pump 10 driven by the engine E is connected to the closed circuit through a charge hydraulic line Lh having a check valve 11 and through a third hydraulic line Lc having a pair of check valves 3 and 3. Hydraulic oil pumped up by the charge pump 10 from an oil sump 15 and regulated its pressure by a charge pressure relief valve 12 is supplied to the one of the two hydraulic lines La or Lb which has lower pressure through the check valves 3 and 3. And, a fourth hydraulic line Ld having a shuttle valve 4 is connected to the closed circuit. To the shuttle valve 4 is connected a fifth and a sixth hydraulic line which respectively have a high pressure relief valve 6 and a low pressure relief valve 7 and are connected to the oil sump 15. The shuttle valve 4 is a 2-port 3-position selector valve, which is operated in response to a hydraulic pressure difference of the first and second hydraulic lines to connect the one of the first or second hydraulic lines La having higher pressure with the fifth hydraulic line Le as well as to connect the other having lower pressure to the sixth hydraulic line Lf. Therefore, the relief hydraulic pressure of a higher pressure-side line is regulated by the high pressure relief valve 6, and the relief hydraulic pressure of the other lower pressure-side line is regulated by the low pressure relief valve 7. Between the first and the second hydraulic lines La and Lb is provided a seventh hydraulic line Lg through which the both lines can be communicated with each other. The seventh hydraulic line Lg is provided with a clutch valve 5, a flow metering valve to control the opening degree of the line Lg. The clutch valve 5 is actuated by a clutch servo unit 80 which is connected thereto through a link 88. Therefore, the flow metering control of the clutch valve 5 by the actuation of the clutch servo valve 80 can accomplish a clutch control for controlling transmission of driving power from the hydraulic pump P to the hydraulic motor M. Actuators for controlling the speed reduction ratio of the continuously variable speed transmission T by way of the displacement control of the hydraulic motor M are the first and the second ratio control servo units 30 and 50 connected to one another by a link mechanism 40. The hydraulic motor M is a swash plate type axial piston motor whose displacement is varied by the control of swash plate angle by the ratio control servo units 30 and 50. The actuations of the ratio control servo valves 30 and 50 as well and the clutch servo valve 80 are respectively controlled by pairs of solenoid valves 151, 152 and 155, 156 which are duty-ratio-controlled by signals from a controller 100. The controller 100 receives signals corresponding to such as vehicle speed V, engine speed Ne, throttle opening ϑth, swash plate angle ϑtr of the hydraulic motor M, accelerator pedal opening ϑacc operated by a driver, atmospheric pressure Pat, oil temperature To, water temperature Tw and clutch opening ϑcl. The controller 100, based on the above signals, outputs signals for controlling the above solenoid valves to effect desirable traveling control. Here, the engine throttle valve opening ϑth and the accelerator pedal opening ϑacc to actuate the engine throttle valve are parameters representing the driver's intention to accelerate or decelerate. The accelerator pedal opening ϑacc is "full-open" when the accelerator pedal is fully depressed, and "full-close" when fully released. The structures and operations of the above servo units 30, 50 and 80 are described in detail hereinafter. Referring first to the ratio control servo unit 30, 50 shown in FIGS. 1 and 2, the first ratio control servo unit 30 controls the swash plate angle of the hydraulic motor M by the help of the high hydraulic pressure fed from the closed hydraulic circuit of the transmission T through the shuttle valve 4, the fifth line Le and a high pressure line 120. The second ratio control servo unit 50 is connected to the first ratio control servo unit 30 by a link mechanism 40 and controls the operation of the first ratio control servo unit 30. The first ratio control servo unit 30 comprises a housing 31 having a connection port 31a connected to the high pressure line 120, a piston member 32 slidably inserted into the housing 31, and a spool member 34 slidably and coaxially inserted into the piston member 32. The piston member 32 consists of a piston portion 32a formed at its right end and a rod portion 32b coaxially extending leftward. The piston portion 32a is fitted into a cylinder hole 31c of the housing 31 and divides the space inside the cylinder hole 31c into two chambers defining two cylinder chambers 35, 36. The rod portion 32b having a smaller diameter than that of the cylinder hole 31c is inserted into a rod hole 31d which is concentric with the cylinder hole 31c. The right cylinder chamber 36 is covered by a plug member 33a and cover 33b through which the right end of the spool member 34 protrudes. The high pressure line 120 connected to the port 31a is communicated with the left cylinder chamber 35 through a hydraulic line 31b. The piston member 32 is pushed rightward by the hydraulic pressure fed in the left cylinder chamber 35 through the high pressure line 120. A land portion 34a which is inserted in a spool hole 32d is formed at the left end of the spool member 34. A pair of dents 34b with fixed axial widths is formed at the right side of the land portion 34a. A stop ring 37 mounted on the spool member 34 hits against a stop ring 38 mounted on the inside surface of the piston member 32 before the spool member 34 comes out. A drain passage 32e which can connect the right cylinder chamber 35 to the oil sump (not shown) through the spool hole 32d responding to the rightward motion of the spool member 34 and a connection passage 32c which can connect the left cylinder chamber 35 to the right cylinder chamber 36 through the dents 34b responding to the leftward motion of the spool member 34 are formed in the piston member 32. When the spool member 34 is moved rightward, the land portion 34a blocks the connection passage 32c and opens the drain passage 32e. Accordingly the hydraulic pressure fed through the high pressure line 120 is led in the left cylinder chamber 35 and pushes the piston member 32 rightward so that the piston member 32 follows the spool member 34. When the spool member 34 is moved leftward, the connection passage 32c communicates with the right cylinder chamber 36 through the dents 34b and the drain passage 32e is blocked by the land portion 34a. Accordingly the high hydraulic pressure is fed to both the left and right cylinder chambers 35, 36. The piston member 32 is pushed leftward because of the difference in areas where pressure is applied and therefore the piston member 32 is moved so as to follow the spool member 34. When the spool member 34 is held still, the piston member 32 is also held still creating a hydraulic floating state because of pressure balance between the left and right cylinder chambers 35, 36. As aforesaid, when the spool member 34 is moved leftward or rightward, the piston member 32 is moved laterally so as to follow the spool member 34 by the help of the high hydraulic pressure fed through the high pressure line 120. Accordingly the variable displacement of the motor M is controlled by the motion of the spool member 34 since the piston member 32 is connected to the swash plate 73 of the motor M by means of a link member 39. The spool member 34 is linked to the second servo unit 50 by means of a link mechanism 40. The link mechanism 40 includes a first link member 42 being swingable around an axis 42c and having two arms 42a and 42b perpendicular to each other, and a second link member 48 pivotally connected to the arm 42b. The upper end of the arm 42a is pivotally connected to the right end of the spool member 34. The bottom end of the second link member 48 is pivotally connected to a spool member 54 of the second servo unit 50. Therefore when the spool member 54 of the second servo unit 50 is moved up or down, the spool member 34 of the first servo unit 30 is moved rightward or leftward. The second servo unit 50 comprises a housing 51 having ports 51a, 51b to which hydraulic lines 102, 104 are connected respectively, with the spool member 54 vertically slidably fitted in the housing 51. The spool member 54 consists of a piston portion 54a, an end spool portion 54b coaxially extending downward and a rod portion 54c coaxially extending upward therefrom. The piston portion 54a is inserted into a cylinder hole 51c of the housing 51 and divides the space inside the cylinder hole 51c covered by a cover 55 into two chambers defining a rod-side (upper) and a head-side (lower) cylinder chamber 52, 53. The end spool portion 54b is fitted into a rod hole 51d which is concentric with the cylinder hole 51c and extends downward. A spool 58a of a top position detecting switch 58 is projected into a recess 54e formed on the end spool portion 54b. The spool 58a is pushed up along the tapered surface of the recess 54e when the spool member 54 is moved up. Therefore it can be found by the top position detecting switch 58a if the speed reduction ratio has become minimum since the pushed-up spool 58a turns the switch 58 on. Further, the hydraulic lines 102, 104 are communicated with the rod-side and head-side cylinder chambers 52, 53 through the ports 51a, 51b. The spool member 54 is moved up or down by the difference of hydraulic forces applied to the piston portion 54a which are determined based on the differences of hydraulic pressures and of areas where the hydraulic pressures in the cylinder chambers 52, 53 are applied. The up and down motions of the spool member 54 are transmitted to the spool member 34 of the first servo unit 30 by the link mechanism 40 causing left and right motions of the spool member 34. In other words, the control of the hydraulic pressures supplied through the hydraulic lines 102, 104 enables control of the motion of the spool member 34 and the piston member 32 in the first servo unit 30 and also enables control of the swash plate angle of the hydraulic motor M and the displacement thereof. In fact, when the spool member 54 of the second servo unit 50 is moved up, the piston member 32 of the first servo unit 30 is moved rightward lessening the swash plate angle, the displacement of the hydraulic motor M and the speed reduction ratio. The pressurized oil in the hydraulic line 102 connecting the port 51a to the rod-side cylinder chamber 52 is sent through a hydraulic line 101 and 102 from the delivery line of the charge pump 10 after its pressure is regulated by the charge pressure relief valve 12. The oil pressure in the hydraulic line 104 connecting the port 51b to the head-side cylinder chamber 53 is obtained by regulating the oil pressure in a hydraulic line 103 (including an orifice 103a therein), which is branched from the hydraulic line 102, by the first and second duty-ratio-controlled solenoid valves 151 and 152. The first solenoid valve 151 duty-ratio-controls the flow rate of the oil flowing from the hydraulic line 103 (having the orifice 103a therein) to the hydraulic line 104. The second solenoid valve 152 is disposed between a hydraulic line 105 branched from the line 104 and a hydraulic line 106 communicating with the drain through an orifice 106a, and duty-ratio-controls drain-flow of the hydraulic oil from the line 104 in accordance with a given duty ratio. The hydraulic lines 101, 102 correspond to the first hydraulic line as defined in claims, and the hydraulic lines 103, 104 to the second hydraulic line as defined in claims. As a result, to the rod-side cylinder chamber 52 a charge pressure regulated by the charge pressure relief valve 12 is applied through the line 102, while to the head-side cylinder chamber 53 is supplied from the line 104 a lower pressure than the charge pressure which is regulated by the first and second solenoid valves 151 and 152. In this connection, since the pressure applied area of the rod-side cylinder chamber 52 is smaller than that of the head-side cylinder chamber 53, the forces of oil pressures in the cylinder chambers 52 and 53 acting on the spool member 54 keep their balance when the oil pressure in the head-side cylinder chamber 53 is a specified value P1 which is smaller than the oil pressure Pu in the rod-side cylinder chamber 52 (Pu > P1). Therefore, when the oil pressure supplied into the head-side cylinder chamber 53 from the line 104 is controlled by the first and second solenoid valves 151 and 152 so as to be higher than the above pressure P1, the spool member 54 is moved upward to have a small swash plate angle of the hydraulic motor M, i.e., to have a small speed reduction ratio, while when the oil pressure supplied into the head-side cylinder chamber 53 from the line 104 is controlled so as to be smaller than the above pressure P1, the spool member 54 is moved downward to have a big swash plate angle of the hydraulic motor M, i.e., to have a big speed reduction ratio. Both solenoid valves 151 and 152 are controlled by signals from the controller 100: only by controlling the operations of the two solenoid valves 151 and 152 based on the signals from the controller 100, the actuations of the first and second ratio control servo units 30 and 50 are controlled, which results in the control of the displacement of the hydraulic motor M, in other words the control of speed reduction ratio. The first and second orifices 103a and 106a each provided in the hydraulic lines which is under duty ratio control by said first and second solenoid valves 151 and 152 are provided as a fail-safe measure in case both the solenoid valves 151 and 152 fail to operate and become OFF. For this purpose the flow passage area A₁ of the first orifice 103a is made not only greater than the similar area A₂ of the second orifice 106a (A₁ > A₂) but also chosen as follows. Firstly, when both the solenoid valves 151 and 152 fail to operate due to malfunction or electrical failure falling into OFF state, the working fluid oil in the hydraulic line 103 flows into the hydraulic line 104 through the first orifice 103a and further flows into the drain (oil sump 15) from hydraulic line 106 through the second orifice 106a. Since A₁ > A₂, the hydraulic pressure Pa in the hydraulic line 104 becomes lower than the pressure Pu in the hydraulic lines 103 and 102, and the pressure Pa can be set at an arbitrary magnitude depending upon the ratio of the two flow passage areas A₁ and A₂. For example, if the ratio (A₁/A₂> is increased, the pressure Pa in the hydraulic line 104 approaches the pressure Pu in the hydraulic lines 102, while the pressure Pa approaches zero when the ratio is decreased. Thus, when both the solenoid valves 151 and 152 become for example OFF, by adjusting this ratio so that the pressure Pa in the hydraulic line 104 becomes a little higher than said predetermined value Pl, the pressure Pu acts in the rod-side cylinder chamber 52 of the second ratio control servo unit 50 and the pressure Pa acts in the head-side cylinder chamber 53. Hence the spool member 54 receives greater pressure from the head-side cylinder chamber 53, the spool member 54 is thereby moved upward to increase the speed reduction ratio (i. e. the ratio is varied towards LOW). It is noted, however, that the force acting on the spool member 54 upwardly is small because the pressure Pa in the head-side cylinder chamber 53 is higher than the pressure Pl only slightly, and therefore that spool member 54 is moved upward slowly and the speed reduction ratio is varied slowly towards LOW. In this manner slow change in the speed reduction ratio towards LOW will provide a fail-safe function even when both of the solenoid valves 151 and 152 become OFF due to, say malfunction during driving. Although only an example is shown above in which the pressure Pa in the hydraulic line 104 (or pressure in the head-side cylinder chamber 53) is set a little higher than the predetermined pressure Pl, the pressure Pa may alternatively be set a little lower than Pl so that when the two valves 151 and 152 become OFF, the spool member 54 is slowly moved downward to gradually change the speed reduction ratio towards TOP (HIGH) as a fail-safe. The following is a detailed description of the construction of the clutch servo unit 80 based on FIG. 3. The clutch servo unit 80 consists of a cylinder member 81, a piston member 82 inserted in the cylinder member 81 slidably to the right and left, a cover member 85 fixed to cover the cylinder chamber into which the piston member 82 is inserted, and a spring 87 pushing the piston member 82 to the left. A piston 82a on the piston member 82 divides aforesaid cylinder chamber 81 into a head-side (left) cylinder chamber 83 and a rod-side (right) cylinder chamber 84 to both of which hydraulic lines 112 and 110 are respectively connected via respective ports 86a and 86b. The hydraulic oil in the hydraulic line 110 is transferred from the charge pump 10 (whose delivery pressure is regulated by the charge pressure relief valve 12) through a hydraulic line 101, while the hydraulic oil in the hydraulic line 112 is transferred from the hydraulic line 101 through a hydraulic line 111, when the hydraulic oil is diverged into the line 111 and passes through an orifice 111a in the line 111, hydraulic oil pressure is controlled by the two duty-ratio-controlled solenoid valves 155 and 156. Here, the solenoid valve 156 is provided to control the flow rate of the hydraulic oil flowing from the line 111 (having the orifice 111a therein) to the line 112 based on the duty ratio signals, while the solenoid valve 155 is disposed between a hydraulic line 113 diverging from the line 112 and a hydraulic line 114 communicating with the drain through an orifice 114a, to control the flow of the hydraulic oil from the line 113 to the drain based on the duty signals. The hydraulic lines 101, 110 correspond to the first hydraulic line as defined in claims, and the hydraulic lines 111, 112 to the second hydraulic line as defined in claims. Therefore, to the rod-side cylinder chamber 84 via the line 110 is applied the charge pressure regulated by the charge pressure relief valve 12, while to the head-side cylinder chamber 83 is applied a pressure from the line 112 lower than the charge pressure, by the action of the aforesaid two solenoid valves 155 and 156. In this connection, the force applied on the piston member 82 from the right side (that is, a force due to the hydraulic pressure P1 in the rod-side cylinder chamber 84 plus the force of the spring 87) balances with the force applied on the piston member 82 from the left side (that is, a force due to the hydraulic pressure P2 in the head-side cylinder chamber 83), even when P2 is lower than P1, because the area of the rod-side cylinder chamber 84 subject to oil pressure is designed to be much smaller than that of the head-side cylinder chamber 83. Therefore, if the solenoid valves 155 and 156 control the hydraulic pressure (in the head-side cylinder chamber 83) supplied from the line 112 so as to be larger than the pressure P2, the piston member 82 will be moved to the right, while when the solenoid valves 155 and 156 control the hydraulic pressure in the head-side cylinder chamber 83 supplied from the line 112 so as to be smaller than the pressure P2, the piston member 82 will be moved to the left. The movement of the piston member 82 to the left or right is transmitted to the clutch valve 5 through a link 88. The clutch valve 5 consists of a stationary member 5a having a first valve port 5b therein, and a rotary member 5c having a second valve port 5d rotatably inserted in the stationary member 5a. An arm 5e engaging with the rotary member 5c is connected to the aforesaid link 88, thus allowing a rotation of the rotary member 5c in accordance with the movement of the aforesaid piston member 82. When the rotary member 5c is rotated, the communication between the first and second valve ports 5b and 5d varies from "fully open" to "fully closed". When the piston member 82 is moved to the leftmost as shown in Fig.2, the communiction in the clutch valve 5 is "fully open", while as the piston member 82 moves to the right, the communication varies gradually to "fully closed" Because the first valve port 5b communicates with the first line La and the second valve port 5d communicates with the second line Lb constituting the hydraulic closed-circuit, the variation in the communication between the aforesaid first and second valve ports 5b and 5d can change the opening degree of the seventh line Lg or the short circuit line of the first and second lines La and Lb, thus effecting clutch control. In other words, based on signal from the controller 100, duty-ratio control of aforesaid solenoid valves 155 and 156 can perform a successful clutch control. The first and the second orifices 111a and 114a provided in said hydraulic line 111 and 114, respectively, are also for securing fail safe in the case of malfunction of the solenoid valves 155 and 156, similar in nature to the orifices 103a and 106a for the speed control servo units 30 and 50, respectively. For this purpose, the flow passage area A₃ of the first orifice 111a is made greater than the similar area A₄ of the second orifice 114a and the ratio of the two areas (A₃/A₄) can be set at a preferable value Therefore, when the two solenoid valves 155 and 156 becomes OFF simultaneously, the piston member 82 of the clutch servo unit 80 is slowly moved to the right by setting the ratio (A₃/ A₄) such that the pressure P₂ in the hydraulic line 112 becomes a little higher than said predetermined pressure P₈. In such a case, the clutch valve 5 will be gradually closed for fail-safe even if the solenoid valves 155 and 156 for the clutch servo units 80 fail to operate during driving. With the above unit, when the clutch valve 5 is closed making the clutch ON in case of solenoid valve malfunction, the vehicle can be stopped by selecting neutral range and it can be run by selecting running range. Alternatively, the clutch valve 5 may be fully opened to make the clutch OFF in case of malfunction and the brake is effected to stop the vehicle. To do this, the pressure P₂ in the hydraulic line 112 is set a little lower than the predetermined pressure P₈ so that piston member 82 is gradually moved to the left, to thereby open the clutch valve 5 slowly when the both of the solenoid valves 155 and 156 has become OFF. Since in accordance with the above constitution the hydraulic servo units for controlling speed reduction ratio and clutch for a continuously variable speed transmission can be controlled by means of only two duty-ratio-control solenoid valves, a control apparatus utilizing such servo unit and consequently the continuously variable speed transmission as well can be made compact and simple in structure, and their manufacturing cost can be reduced also. In what follows other embodiments of the invention are described with reference to FIG. 4. FIG. 4 is a schematic diagram of the hydraulic circuit for a continuously variable speed transmission having a control apparatus according to the invention, in which those portions similar to those shown in FIG. 1 are numbered the same as in FIG. 1 and the description thereof are not repeated. An output shaft 28 connected to the wheels W is placed in parallel with the drive shaft 2 of the hydraulic motor M. A directional change gear unit 20 is placed between these two shaft 2,28. This gear unit 20 comprises a first and a second drive gear 21,22 firmly mounted on the drive shaft 2 leaving an axial space therebetween, a first driven gear 23 rotatably mounted on the output shaft 28 and engaged with the first drive gear 21, a second driven gear 25 rotatably mounted on the output shaft 28 and engaged with a intermediate gear 24 which is engaged with the second drive gear 22, a clutch hub 26 placed between the first and second driven gears 23, 25 and firmly mounted on the output shaft 28, and a sleeve 27 slidably mounted on the clutch hub 25 which can be selectively engaged with the clutch gears 23a, 25a formed on the sides of the driven gears 23, 25. In the directional change gear unit 20, when the sleeve 27 is slid leftward, the clutch gear 23a of the first driven gear 23 is connected to the clutch hub 25 by means of the sleeve 27 (as shown in Fig. 1). Hence the rotational direction of the output shaft 28 is opposite to that of the drive shaft 2 and the wheels W are driven forward by the continuously variable speed transmission T. On the other hand, when the sleeve 27 is slid rightward, the clutch gear 25a of the second driven gear 25 is connected to the clutch hub 25 by means of the sleeve 27. Hence, the rotational direction of the output shaft 28 is the same as that of the drive shaft 2 and the wheels W are driven rearward. The directional change servo unit 60 provides directional change operation by sliding the sleeve 27 of said directional change gear unit 20 (See FIG. 5). The control of this directional change servo unit 60 is given by a manual valve (or shift valve) 90 which supplies/extracts working fluid in association with the motion of the shift lever. The directional change servo unit 60 comprises a housing 61 having four ports 62a, 62b, 62c, 62d with which four hydraulic lines 123, 124, 125a and 125b shown in FIG. 4 are connected, and a spool member 65 which is slidably inserted in the housing 61 for longitudinal motion therein. The spool member 65 consists of a piston portion 65a and a rod portion 65 extending rightward therefrom coaxially with the piston portion. The piston portion 65a is inserted in the cylinder bore 61a which is formed in the housing 61 to extend longitudinally, and divide the cylinder chamber surrounded by the cover 67 cylinder chamber 63 and right cylinder chamber 64. The rod portion 65b is inserted in a rod bore 61b which extend to the right coaxially with the cylinder bore 61a, the right end thereof extends out of the right end surface of the housing 61 and has a shift fork 68 mounted thereon which engages with the sleeve 27 of the directional change unit 20 to slidably shift the sleeve. In the spool member 65 is a communication bore 65c so formed to axially extend and open at its left end to communicate with the left cylinder chamber 63. A valve bore 65d is also formed in the spool member, which extends from the bore 65c to its opening on the outer surface of the rod portion 65b. The spool member 65 is biased to the left by a spring 66 mounted inside the right cylinder chamber 64. The servo unit 60 having the above constitution is operated by means of a hydraulic pressure supplied in response to the operation of the manual valve 90 from the hydraulic lines 123 and 124 to the right and left hydraulic pressure chamber 63 and 64, respectively. The hydraulic line 123 communicates with the reverse port 94 of the manual valve 90 while the hydraulic line 124 communicates with the forward port 92 thereof. The manual valve 90 operates in accordance with the motion of the shift lever in the driver's compartment which controls the motion of the spool 95. When the shift lever is positioned in the "D" or "L" range for forward running, the valve 90 connects the input port 91 with the forward port 92; when the shift lever is positioned in the "R" range, it connects the input port 91 with the reverse port 94; and in "N" range (neutral range), it shuts the input port 91 and connects the forward port 92 and the reverse port 94 with the drain. "D, L, R" ranges are referred to as running ranges. The input port 91, via hydraulic line 101, communicates with charge hydraulic line Lh whose pressure is regulated by a charge pressure relief valve 12. Consequently, when the shift lever is in the forward range (D or L range), the reverse port 94 communicates with the drain in the manual valve 90, while the forward port 92 communicates with the input port 9. Then, the left cylinder chamber 63 of the directional change servo unit 60 communicates with the drain, and to the right chamber 64 is supplied the charge pressure from the charge hydraulic line Lh. As a result the hydraulic pressure in the right cylinder chamber 64 forces the spool member 65 to the left, the shift fork 68 to the left, and also the sleeve 27 (FIG. 4) engaging therewith to the left, thereby setting the directional change gear unit 20 at forward range. The right cylinder chamber 64 then communicates via a notch 65e of the spool member 65, with a (communication) line 69a communicating with the port 62c, so that the hydraulic pressure in the right cylinder chamber 64 (charge hydraulic pressure) is also supplied from the port 62c to the hydraulic pressure line 126 through the hydraulic line 125b. As the shift lever is shifted to "N" position, the input port 91 is shut and other ports 92, 93, and 94 are connected with the drain (shown in FIG. 4). The hydraulic pressures in the right and left cylinder chambers 63 and 64 of the directional change unit fall to "0", but the spool member 65 is held in the left biased position by the biasing force of the spring 66, which retains the directional change gear unit in the forward condition. To note, the hydraulic pressure in the hydraulic line 126 is also "0". When the shift lever is shifted to "R", the input port 91 communicates with the reverse port 94, while other ports 92 and 93 remain communicating with the drain. Under such conditions, to the left cylinder chamber 63 is provided the hydraulic pressure from charge hydraulic line Lh, and, since the right cylinder chamber 64 communicates with the drain, the spool member 65 is moved to the right and the shift fork 68 is also moved to the right to move the sleeve 27 to the right, resulting in the switching of the gears in the directional change unit 20 from rearward to forward arrangement. The valve port 65d of the spool member 65 has an opening in the communication line 69b connected with the port 62d. The hydraulic pressure in the left cylinder chamber 63 (charge hydraulic pressure) is also supplied via the hydraulic line 126 to the communication bore 65c, valve bore 65d, communication line 69b and the hydraulic pressure line 125a. On the other hand, the operation control of the clutch valve 5 is given by the clutch servo unit 80 shown in FIG. 6. The operation of the clutch servo unit 80 is controlled by a pair of solenoid valves 155 and 156 whose duty ratios are in turn controlled in response to signals given by the controller 100. The controller 100 receives signals representing vehicle speed V, rotational engine speed Ne, throttle opening ϑth, inclination angle ϑtr of the hydraulic motor M, and accelerator opening ϑacc, and generates signals to control said solenoid valves 155 and 156 so that desired driving control can be attained. The clutch servo unit 80 shown in FIG. 6 has the same structure as that shown in FIG. 3, wherein the head-side cylinder chamber 23 is connected with the hydraulic line 128 and the rod-side cylinder chamber 84 with the hydraulic line 122. The hydraulic line 122 branches from the hydraulic line 101 and communicates with the charge hydraulic line Lh, to which the charge pressure regulated by a charge pressure relief valve 12 is supplied. The hydraulic pressure in the hydraulic line 128 is obtained by controlling the pressure supplied from the hydraulic line 127 having an orifice 127a, which branches from said hydraulic line 126, by the first and second solenoid valves 155 and 156 which are under duty ratio control. The first solenoid valve 156 is for controlling the flow rate of the working fluid passing from the hydraulic line 127 having orifice 127a to the hydraulic line 128 in accordance with the duty ratio. The second solenoid valve 155, arranged between the hydraulic line 129 which branches from the hydraulic line 128 and the hydraulic line 130 that communicates with the drain via an orifice 130a, controls the out going flow of the oil from the hydraulic line 129 to the drain in accordance with the duty ratio. From the hydraulic line 126 branches a hydraulic line 131 which communicates with the hydraulic line 128. The hydraulic line 131 is provided with a check valve 140 consisting of a ball 21 and a spring 22 which permits the flow from the hydraulic line 128 to the hydraulic line 126, but prohibits the flow in the opposite direction. The hydraulic lines 101 and 122 correspond to the first hydraulic line in claims, and the hydraulic lines 101 to 124 (or alternatively lines 123, 126, 127 and 128) correspond to the second hydraulic line, while the hydraulic line 131 corresponds to the hydraulic branch line. Therefore, the rod-side cylinder chamber 84 is always supplied with charge hydraulic pressure from the hydraulic line 101 and 122. On the other hand, when the running range is selected in the transmission, the head-side cylinder chamber 83 is supplied with a charge hydraulic pressure through the hydraulic line 126 by means of the manual valve 90, but is not supplied with the charge hydraulic pressure when the transmission is in the neutral range, making the hydraulic pressure in the head-side cylinder chamber 83 zero. Furthermore, even when the transmission is in the running range, the head-side cylinder chamber 83 is not supplied with the charge hydraulic pressure in the hydraulic line 126 directly, but supplied with the pressure only after it is reduced to a pressure lower than the charge pressure by the first and second solenoid valves 155 and 156. The pressure applied area of the piston portion 82a is smaller in the rod-side cylinder chamber 84 than in the head-side cylinder chamber 83 so that the forces acting on the piston due to the pressures in both chamber 83 and 84 and the biasing force of the spring 87 are balanced when the hydraulic pressure P₂ in the head-side cylinder chamber 83 is lower than the pressure P1 in the rod-side cylinder chamber 84 (P1 > P2). Consequently, by raising the hydraulic pressure supplied from the hydraulic line 128 to the head-side cylinder chamber 83 higher than P2, piston member 82 can be moved to the right, while by reducing the pressure supplied at the head-side cylinder chamber 83 lower than P2 the piston member 82 can be moved to the left. The rightward and leftward motion of the piston member 82 is transmitted to the clutch valve 5 through the link mechanism 88, providing as before clutch control. The constitution of the clutch valve 5 is the same as the one shown in FIG. 3, and its description is not repeated. The operation of such continuously variable speed transmission is now described. When the manual valve 90 is in the neutral position as set by the shift lever, the hydraulic pressures in the hydraulic lines 123, 124 and 126 are all zero, so that the spool member 65 of the directional servo unit 60 is shift leftward by the action of the spring 66 to set the directional change gear unit 20 at the forward position, and also the piston member 82 of the clutch servo unit 80 is shift leftward to fully open the clutch valve 5. Under this condition the hydraulic motor M is not rotated and remains neutral while the hydraulic pump P has been driven by the engine E. As the manual valve 90 is switched from the above range to, for example, "D" range by means of the shift lever, the charge hydraulic pressure is supplied to the hydraulic lines 124 and 126. Upon this switching although the directional change gear unit 20 remains at the forward position, the head-side cylinder chamber 83 of the clutch servo unit 80 is provided with a pressure that is determined by the solenoid valves 155 and 156, and as a result the opening control of the clutch valve 5 is conducted. The opening control of the clutch valve 5 is for permitting smooth starting/stopping of the vehicle. This may be done, for example, by establishing reference clutch openings in relation to the engine throttle opening and the vehicle speed, and by giving the first and second solenoid valves 155 and 156 duty ratio signals supplied by the controller 100 such that the reference clutch opening can be obtained corresponding to the actual throttle opening and vehicle speed. When the shift range is "D" under the controlled opening of the clutch valve 5, the clutch valve 5 is opened to prevent engine stalling if the acceleration pedal is not depressed, leaving the engine idling. As the acceleration pedal is thereafter depressed, the opening control of the clutch valve 5 is carried out as described above to turn the clutch ON, and the vehicle will be started (and put to a running condition). In stopping the vehicle, as the vehicle speed becomes lower than the predetermined speed, the controller generates a signal which is transmitted to the solenoid valves 155 and 156 for opening the clutch valve 5 to turn the clutch OFF. When the vehicle is at a halt, the clutch is set OFF (by opening the clutch valve 5) to thereby prevent engine stall. However, if the solenoid valves 155 and 156 stop their operation on account of malfunction of the controller 100, or sticking of spools of the solenoid valves 155 and 156 during running while they are in ON condition, the fluid in the head-side cylinder chamber 83 is trapped and the clutch valve 5 is shut, leaving the clutch ON. If the vehicle is stopped with the clutch left in this condition, the engine suffers from an over load since the engine tends to drive the wheels through the continuously variable speed transmission T, and finally incurs engine stall. In this case, the ball 141 is pushed by the charge hydraulic pressure in the hydraulic line 126 so that the check valve 140 remains shut and the fluid is not let out through the hydraulic line 131. Nevertheless, in the event that both of the solenoid valves 155 and 156 malfunction in ON state, if the manual valve 90 is switched to the neutral range by shifting the shift lever, the hydraulic line 126 communicates with the drain, thereby releasing the ball 141 of the check valve 140 due to the hydraulic pressure in the head-side cylinder chamber 83 to overcome the spring 22 and the fluid in the head-side cylinder chamber 83 is exhausted into the drain through the hydraulic line 131. At the same time, because of the hydraulic pressure in the rod-side cylinder chamber 84, the piston member 82 is moved to the left to fully open the clutch valve 5. Namely, in the case of simultaneous failure of solenoid valves 155 and 156 remaining in ON state, engine stall can be avoided by moving the shift lever in the neutral range to make the clutch OFF. Although the invention has been described in the above for the control of a clutch servo valve used with a continuously variable speed transmission, it is not limited thereto, but may be utilized equally well for controlling clutches of the transmission of different types by means of the servo valves according to the invention. As has been described above, when the first and second solenoid valves have failed simultaneously to control the clutch servo valve units, remaining in ON state, the working fluid is trapped in the head-side cylinder chamber and the servo cylinder is immobilized as it is. However, by operating the shift lever from the running range to neutral range, the second hydraulic line on the side of the pressure supply source is shut and the second hydraulic line on the side of the branching portion is adapted to communicate with the drain by means of the shift valve (i.e. manual valve), the head-side cylinder chamber communicates by the action of the check valve with the drain through the branching hydraulic line and the shift valve, which permits the servo valve to move making the clutch turned OFF to avoid stalling of the engine.

Claims: A control apparatus for a hydraulic servo unit comprising a cylinder and a piston inserted in a chamber formed in said cylinder, said piston having a piston portion which is slidably inserted in said cylinder chamber and a rod portion with one end thereof being fast with said piston portion and the other end thereof extending out of said cylinder chamber, said cylinder chamber being divided by said piston portion into a rod-side cylinder chamber (52) through which said piston rod penetrates and a head-side cylinder chamber (53) to which the end surface of said piston portion faces, a pressure receiving area of said head-side cylinder chamber being greater than a pressure receiving area of said rod-side cylinder chamber; the control apparatus comprising: a first hydraulic line (102; 101, 122) for supplying a working fluid of predetermined pressure from a hydraulic pressure source to said rod-side cylinder chamber; a first solenoid valve (151; 156) whose opening is controlled in accordance with duty ratio signals; a second hydraulic line (104; 126, 124, 101) for enabling a connection between said head-side cylinder chamber and said first hydraulic line via at least said first solenoid valve; a second solenoid valve (152; 155) whose opening is controlled in accordance with duty ratio signals; and a drain hydraulic line (106; 130) connecting said head-side cylinder chamber with a drain via said second solenoid valve, wherein a first orifice (103a; 127a) having a predetermined fixed flow passage area (A1) is provided in said second hydraulic line, and a second orifice (106a; 130a) having a predetermined fixed flow passage area (A2) smaller than said area of the first orifice is provided in said drain hydraulic line. A control apparatus as defined in claim 1; wherein said hydraulic servo unit is used for controlling the speed reduction ratio of a continuously variable speed transmission. A control apparatus as defined in claim 1; wherein said hydraulic servo unit is used for controlling the clutch of a continuously variable speed transmission. A control apparatus as defined in any preceding claim further comprising: a shift valve (90) additionally provided in a portion of said second hydraulic line (126) between said first hydraulic line (122) and said first solenoid valve (156); wherein said shift valve shuts the second hydraulic line on a side of said first hydraulic line and connects the second hydraulic line on a side of said first solenoid valve with a drain when a neutral range is selected, but allows working fluid to flow through said second hydraulic line by directly connecting the head-side cylinder chamber and the first hydraulic line via the first solenoid valve when a running range is selected. A control apparatus as defined in any of claims 1 to 3 further comprising: a hydraulic branch line (131) one end of which is connected with a portion of said second hydraulic line between said hydraulic pressure source and said first solenoid valve, and the other end of which is connected with said head-side cylinder chamber; a check valve (140) provided in said hydraulic branch line for permitting the working fluid to flow only from said head-side cylinder chamber into said second hydraulic pressure line at a point by-passing the first solenoid valve, and not permitting the fluid to flow from said second hydraulic pressure line by-passing said first solenoid valve through said hydraulic branch line into said head-side cylinder; and a shift valve (90) additionally provided in a portion of said second hydraulic line between said hydraulic pressure source and a branching point of said branch line; wherein said shift valve shuts the second hydraulic line on a side of said hydraulic pressure source and connects the second hydraulic line on a side of said branching point with a drain when a neutral range is selected, but allows working fluid to flow through said second hydraulic line by directly connecting the head-side cylinder chamber and the first hydraulic line via the first solenoid valve when a running range is selected.

Inventors: MAKI KAZUYA, MIYAKE JUNICHI C O KABUSHIKI K, YAMAGUCHI KOUJI C O KABUSHIKI, MAKI, KAZUYA, MIYAKE, JUNICHI C/O KABUSHIKI KAISHA HONDA, YAMAGUCHI, KOUJI C/O KABUSHIKI KAISHA HONDA
Applicants: HONDA MOTOR CO LTD, HONDA GIKEN KOGYO KABUSHIKI KAISHA
Application year: 1988
Main classification: F16H61
IPC codes: F16H61