Rotary valve for automatic transmission

Abstract: An oil passage (120) is provided in an axially central portion of a spool (7) which is received within a valve housing (1) and rotatively driven by a pulse motor (6), and oil passages (12₁-12₅) passed diametrically through the spool (7) and connected to said oil passage (120), so that a hydraulic pressure from an input port (13) connected to a hydraulic pressure source (S) is selectively supplied to the oil passages (12₁-12₅) for selectively engaging and disengaging frictionally engaging elements of an automatic transmission. An axially acting load provided by the hydraulic pressure is received by a thrust bearing (10) mounted at an end of the spool (7). The supply of oil from the axial portion of the spool enables no side force to be applied, thereby reducing the frictional force and to enhance the sealability between the valve housing (1) and the spool (7).

Description: The invention relates to a rotary valve for an automatic transmission, comprising a spool rotatably received within a valve housing and driven by an actuator for selectively supplying hydraulic pressure from a hydraulic pressure source to each of a plurality of frictionally enganging elements through said spool. Such a rotary valve is described in the generic JP-A 63-312577. This rotary valve suffers from a problem that line pressure supplied from the hydraulic pressure source through an input port formed in the valve housing is applied to an outer side surface of the spool from a radial direction and, for this reason, an opposite outer side surface of the spool is urged against an inner peripheral surface of a valve bore of the valve housing and, as a result, smooth rotation of the spool is prevented. In the known rotary valve, in order to cope with the situation where the spool becomes non-rotatable for any reason, such as, a malfunction of the pulse motor, for rotatively driving the spool and a clogging with dust particles, means for providing small vibration to the spool for preventing any sticking of spool are provided, and an emergency valve is provided. This causes a complication of the structure and an increase in cost. In addition, the spool of the rotary valve includes a plurality of axially arranged oil passages and, therefore, if the distance between adjacent oil passages is diminished, to reduce the axial size, it is necessary to conduct precise axial positioning of the spool. Further, in the known rotary valve, when the hydraulic pressure is being supplied to an intended frictionally engaging element, the hydraulic pressure for the other frictionally engaging elements is released through the rotary valve. The releasing of the hydraulic pressure is carried out through a common path during either downshifting or upshifting. In order to moderate shifting shock during downshifting and upshifting, it is desireable that during upshifting, the releasing of the hydraulic pressure from the frictionally engaging element, which has been in engagement theretofore, is retarded to permit the two engaging elements to be brought into a co-engagement. It is desireable that during downshifting, the releasing of the hydraulic pressure from the frictionally engaging element, which has been in engagement theretofore, is expedited to temporarily produce a neutral condition, thereby increasing the number of revolutions of the engine to a proper extent. In the known rotary valve, however, the path through which the hydraulic pressure is released is common during both upshifting and downshifting and, therefore, it is difficult to provide different dropping characteristics of the hydraulic pressure during upshifting and downshifting. Accordingly, it is an object of the present invention to provide a rotary shaft for an automatic transmission, wherein the spool can be smoothly rotated, and a sealability can be easily insured. To achieve this object the rotary valve of the invention comprises the features as defined in claim 1. Advantageous designs of the rotary valve are described in the subclaims. The above and other objects, features and advantages of the invention will become more apparent from a consideration of the following description of the preferred embodiments, taken in conjunction with the accompanying drawings. BRIEF DESCRIPTION OF THE DRAWINGS Figs. 1 to 8b illustrate a first embodiment of the present invention, wherein Fig. 1 is a longitudinal sectional view of a rotary valve of the first embodiment; Fig. 2 is a sectional view taken along a line 2-2 in Fig. 1; Fig. 3 is a sectional view taken along a line 3-3 in Fig. 1; Fig. 4 is a view similar to Fig. 3, showing the valve in different position; Fig. 5 is a perspective view of a spool of the valve of Fig. 1; Fig. 6 is a view of the development of an outer peripheral surface of the spool of Fig. 5; Figs. 7a to 7e are views taken along lines 7a-7a to 7e-7e, respectively, in Fig. 1; Figs. 8a and 8b are views similar to Fig. 7c, showing the valve in different position; and Figs. 9 to 12 illustrate a second embodiment of the present invention, wherein Fig. 9 is a longitudinal sectional view of a rotary valve of the second embodiment; Fig. 10 is a sectional view taken along a line 10-10 in Fig. 9; Fig. 11 is a sectional view taken along a line 11-11 in Fig. 9; Fig. 12 is an enlarged view of an encircled portion indicated by reference numeral 12 in Fig. 9. DESCRIPTION OF THE PREFERRED EMBODIMENTS The present invention will now be described by way of embodiments in connection with the accompanying drawings. In Fig. 1, reference character V is a rotary valve for an automatic transmission, which functions to selectively supply a hydraulic pressure fed to valve V from a hydraulic pressure source S to each of a plurality of frictionally engaging elements C₁ to C₅ to cause the automatic transmission for an automobile to which valve V is attached to shift to a desired gear shift stage. Rotary valve V is comprised of valve housing 1 having valve bore 1₁ with a circular section at a central portion, cover plate 3, secured by a plurality of bolts 2, to close an opening at a left end of valve housing 1, pulse motor 6, as an actuator, secured to a right end of valve housing 1 by a plurality of bolts 5 passed through mounting flange 4, and a substantially columnar spool 7, rotatably received in valve bore 1₁ in valve housing 1 and rotatively driven by pulse motor 6. As best seen by reference to Figs. 1 and 2, D-shaped chamfered connecting member 9 is spline-coupled to a tip end of output shaft 8 of pulse motor 6 extending into valve housing 1. D-shaped connecting member 9 is engaged in D-shaped recess 7₁, Fig. 1, in a right end face of spool 7. Thus, spool 7 can be rotated, through a predetermined angle within valve bore 1₁ in valve housing 1 by pulse driving pulse motor 6. Thrust bearing 10 is mounted between the right end face of spool 7 and an inner wall surface of valve housing 1. Loads, which urge the spool 7 rightwardly when free rotation of spool 7 is permitted, are received by thrust bearing 10. As can be seen from Figs. 1 and 3, smaller-diameter portion 7₂ is formed at a left end of spool 7, Fig. 1, to define annular space 11 between smaller-diameter portion 7₂ and valve bore 1₁. Central oil passage 12₀ extends through the spool 7 along its rotary axis and opens into the left end face of spool 7, Fig. 1. Recess 3₁, Fig. 1, is provided in cover plate 3 in opposed relation to the left end face of spool 7. Input or oil supply port 13, opening into recess 3₁, connects valve V to the hydraulic pressure source S. Input port 13 and oil passage 12₀ in spool 7 are interconnected through feed pipe 14. More specifically, flange 14₁, formed at a left end of feed pipe 14, Fig. 1, is fitted into recess 3₁ and urged and fixed by annular retainer 15 and clip 16. In this case, a pair of sealing members 17 and 18 are mounted between recess 3₁ and retainer 15. On the other hand, a right end of the feed pipe 14 is inserted into oil passage 12₀ in spool 7 through bushing 19. This ensures that line pressure supplied to the input port 13 from the hydraulic pressure source S can be supplied through feed pipe 14 into oil passage 12₀ in spool 7. As can be seen by reference to Fig. 5 in addition to Figs. 1 to 3, radially extending pin 20 is embedded into the smaller-diameter portion 7₂ of spool 7, while a bolt 21, Fig. 1, is threadedly inserted into valve housing 1 with its tip end reaching the interior of annular space 11. Engaging portions 22₁ and 22₂ are formed at opposite ends of coil spring 22, received in the annular space 11, and are retained between pin 20 and bolt 21. Coil spring 22 is mounted with a load previously provided thereto so as to bias spool 7 in a clockwise rotational direction (a direction indicated by an arrow A in Figs. 3 and 5) and also in an axial direction (a direction indicated by an arrow B in Figs. 1 and 5). A pair of steps 7₃ and 7₄, Fig. 3, are formed at a right end of smaller- diameter portion 7₂, and one of steps 7₃ is adapted to engage bolt 21 to define an end of rotation of spool 7, when spool 7 is rotated by resilient force of coil spring 22. As can be seen from Figs. 1, 5 and 6, spool 7 has five parallel oil passages 12₁ to 12₅ provided therein in an axially parallel arrangement and diametrically passed therethrough to communicate with oil passage 12₀. Spool 7 also has a series of downshifting drain grooves 23a₁ to 23a₅ and a series of upshifting drain grooves 23b₁ to 23b₅ circumferentially provided in an outer peripheral surface thereof in a sandwiching relation to five oil passages 12₁ to 12₅. As can be seen from Figs. 1, 3 and 7a to 7e, five oil passages 24₁ to 24₅ are radially provided in valve housing 1 in correspondence to five oil passages 12₁ to 12₅ provided in axially parallel arrangement in spool 7. Oil passages 24₁ to 24₅ are radially formed at distances from one another in an axial direction of the valve bore 1₁ and at different phases through a predetermined angle, and an opening at an outer end thereof is occluded by plug 25. Oil passages 24₁ to 24₅ communicate with output ports 27₁ to 27₅ opened in cover plate 3 through oil passages 26₁ to 26₅ axially provided in valve housing 1. Output ports 27₁ to 27₅ are connected to frictionally engaging elements C₁ to C₅ of the automatic transmission, not shown, for establishing first to fifth gear shift stages (only the frictionally engaging element C₃ for the third gear shift stage being diagrammatically shown in Fig. 1), respectively. As shown in Figs. 7a to 7e, downshifting drain ports 28a₁ to 28a₅ and upshifting drain ports 28b₁ to 28b₅ are provided in pairs in valve housing 1 on a diametrical line and opened into valve bore 1₁. Downshifting drain ports 28a₁ to 28a₅ always communicate with downshifting drain grooves 23a₁ to 23a₅ within a range of rotation during operation of spool 7, and upshifting drain ports 28b₁ to 28b₅ likewise always communicate with upshifting drain grooves 23b₁ to 23b₅ within a range of rotation during operation of spool 7. Outer ends of drain ports 28a₁ to 28a₅ and 28b₁ to 28b₅ communicate with downshifting hydraulic pressure control means Vd and upshifting hydraulic pressure control means Vu for adjusting the hydraulic pressure released from these drain ports. Each of hydraulic pressure control means Vd and Vu is comprised, for example, of a solenoid valve, an orifice, or a combination of a solenoid valve and an orifice. Downshifting hydraulic pressure control means Vd operates to expedite releasing of hydraulic pressure from frictionally engaging elements C₂ to C₅ while upshifting hydraulic pressure control means Vu operates to retard releasing of hydraulic pressure from frictionally engaging elements C₁ to C₄. The first embodiment of the present invention having the above-described construction will be described below. When spool 7 is, for example, in a position corresponding to a third gear shift, as shown in Figs. 1 and 7c (such position being referred to as a third gear shift position hereinafter), line pressure supplied to input port 13 from hydraulic pressure source S is passed through feed pipe 14 to oil passage 12₀, axially provided in spool 7, and transmitted from oil passage 12₀ through radially extending oil passage 12₃, oil passage 24₃ radially extending in valve housing 1 and oil passage 26₃, axially extending in valve housing 1, to output port 27₃. This causes frictionally engaging element C₃ of the automatic transmission, not shown, connected to output port 27₃ to be operated to establish the third gear shift stage. During this time, the other four output ports 27₁, 27₂, 27₄ and 27₅ are connected to drain ports 28b₁, 28b₂, 28a₄ and 28a₅, formed in valve housing 1, through oil passages 26₁ 26₂, 26₄ and 26₅; 24₁, 24₂, 24₄ and 24₅ and the drain grooves 23b₁, 23b₂, 23a₄ and 23a₅ formed in spool 7. In other words, when spool 7 is in the third gear shift position, input port 13 is connected only to output port 27₃ of the five output ports 27₁ to 27₅. When upshifting, for example, from the third gear shift stage to the fourth gear shift stage is desired, spool 7 is driven clockwise, in the direction of arrow A in Fig. 7c by pulse motor 6 for rotation to a fourth gear shift position shown in Fig. 7d. Then, input port 13 is put out of communication with output port 27₃ and, at the same time, newly connected to output port 27₄, through oil passages 12₀ and 12₄ in spool 7 and oil passages 24₄ and 26₄ in valve housing 1, so that line pressure is supplied to hydraulically engaging element C₄, thus establishing the fourth gear shift stage in the automatic transmission. As shown in Fig. 8a, the hydraulic pressure for frictionally engaging element C₃ to which the line pressure has been supplied theretofore is released from upshifting drain port 28b₃ through output port 27₃, the oil passages 26₃ and 24₃ and the upshifting drain groove 23b₃. During this time, the releasing of the hydraulic pressure entering upshifting drain port 28b₃ is retarded by the upshifting hydraulic pressure control means Vu and, hence, the co-engagement of both the frictionally engaging element C₃ for the third gear shift and the frictionally engaging element C₄ for the fourth gear shift is produced, thereby moderating the shifting shock during upshifting. Even when the upshifting from any gear shift stage is conducted, spool 7 is certainly rotated in the direction of arrow A and, therefore, the hydraulic pressure for corresponding one of frictionally engaging elements C₁ to C₄ which has been in engagement theretofore is always released into corresponding one of upshifting drain ports 28b₁ to 28b₄, thus providing an effect similar to that described above. To the contrary, when downshifting, for example, from the third gear shift stage to the second gear shift stage is desired, spool 7 is driven in a counterclockwise direction, indicated by an arrow C in Fig. 7c, by the pulse motor 6 for rotation to a second gear shift position shown in Fig. 7b. Input port 13, Fig. 1, is put out of communication with output port 27₃ and, at the same time, newly connected to output port 27₂ through oil passages 12₀ and 12₂ in spool 7 and oil passages 24₂ and 26₂ in valve housing 1, so that the line pressure is supplied to hydraulically engaging element C₂ of the transmission, not shown, thus establishing the second gear shift stage in the automatic transmission. As shown in Fig. 8b, the hydraulic pressure for frictionally engaging element C₃, to which the line pressure has been supplied theretofore, is released from the downshifting drain port 28a₃ through the output port 27₃, Fig. 1, oil passages 26₃ and 24₃ and downshifting drain groove 23a₃. The releasing of the hydraulic pressure from downshifting port 28a₃ is expedited by the downshifting hydraulic pressure control means Vd and, hence, a neutral condition is temporarily produced, ensuring that the number of revolutions of engine can be increased to a proper extent. This makes it possible to moderate the shifting shock during downshifting. For the downshifting, the spool 7 is necessarily rotated in the counterclockwise direction, as shown by the arrow C even during the downshifting from any gear shift stage. Therefore, the hydraulic pressure for corresponding one of frictionally engaging elements C₂ to C₅, which has been in engagement theretofore, is always released into corresponding one of downshifting drain ports 28a₂ to 28a₅, thus providing an effect similar to that described above. When rotary valve V is in operation in the above-described manner, the line pressure from hydraulic pressure source S is supplied through input port 12 and feed pipe 14 to oil passage 12₀, axially formed in spool 7, so that spool 7 is urged rightwardly as viewed in Fig. 1 by the line pressure. During this time, side force on spool 7 is eliminated, because radiate oil passage 12₁ to 12₅, communicating with central oil passage 12₀, are defined axially symmetrically to diametrically extend through spool 7. This causes no radial urging of spool 7 thereby avoiding a large frictional force between spool 7 and valve bore 1₁ in valve housing 1. Spool 7 is also urged rightwardly by the force of coil spring 22, but axially rightward load is received by thrust bearing 10 mounted at the right end, Fig. 1, of spool 7 and, therefore spool 7 can be smoothly rotated by a slight driving force. Moreover, spool 7, biased rightwardly, is axially positioned by means of thrust bearing 10 and, hence, oil passages 12₁ to 12₅ in spool 7 are automatically aligned with oil passages 24₁ to 24₅ in valve housing 1. In addition, the line pressure supplied through feed pipe 14 to spool 7 is sealed by bushing 19 mounted between feed pipe 14 and oil passage 12₀. Moreover, such line pressure is supplied from the axial end of spool 7 and, therefore, a short-circuiting between oil passage 12₀ and the other oil passages 12₁ to 12₅ is prevented. If pulse motor 6 should break down and fail to drive spool 7, spool 7 is rotated by the resilient force of coil spring 22, mounted between spool 7 and valve housing 1, and stopped at a position shown in Fig. 4 in which the step 7₃, formed in spool 7, abuts against bolt 21, i.e., at a position corresponding to a fifth gear shift, the highest gear shift stage of the automatic transmission, not shown. Even when spool 7 is not rotated smoothly, due to a malfunction of pulse motor 6 or a clogging with dust particles, spool 7 can be automatically rotated to the fifth gear shift position by detecting an abnormality, by a proper sensor, to cut off the energization of pulse motor 6. It should be noted that the target position to which spool 7 is rotated by the force of coil spring 22 is not limited to fifth gear shift position and may be a position corresponding to a higher gear shift, e.g., a position corresponding to a fourth gear shift. If rotary valve V has a neutral position, spool 7 may be rotated toward such neutral position. When each of the hydraulic pressure control means Vd and Vu is comprised of an orifice, in the above-described embodiment, if the orifice of the downshifting hydraulic pressure control means Vd is of a relatively large diameter, while the orifice of the upshifting hydraulic pressure control means Vu is of a relatively small diameter, it is possible to retard the dropping of the hydraulic pressure during upshifting and to expedite the dropping of the hydraulic pressure during downshifting, by the operation of such orifices. Further, both orifices can be connected, at their downstream portions to a common oil passage, and a solenoid valve can be provided in such common oil passage, thereby finely adjusting the dropping characteristic of hydraulic pressure. With such construction, the dropping characteristic of hydraulic pressure can be, of course, insured by the operation of the orifices, even if the solenoid valve breaks down. A second embodiment of the present invention will be described below in connection with Figs. 9 to 12. In this embodiment, coil spring 22 has not an axial preset load, but has only a preset load in a rotational direction. Ball carrying member 29, Figs. 10 and 12, is mounted on a left end face of spool 7, and a ball 31, Fig. 10, is carried in ball carrying member 29 and biased leftwardly, as viewed in Fig. 12, by a force of spring 30. On the other hand, retainer 15, mounted to cover plate 3, has five recesses 15₁ to 15₅ circumferentially provided therein and engageable by ball 31. A click stop mechanism is formed by ball 31 biased by spring 30 and recesses 15₁ to 15₅ in retainer 15. With this embodiment, when spool 7 is stopped at any of the first to fifth gear shift positions, ball 31 engages one of the recesses 15₁ to 15₅ to precisely position spool 7. Moreover, spool 7 is biased rightwardly by reaction of resilient force of spring 30 urging ball 31 and, hence, spool 7 can be urged against thrust bearing 10 in cooperation with a rightward load by the line pressure and, thus, positioned axially. It will be appreciated that even if ball 31 may be carried in valve housing 1 and engaged into a recess provided in spool 7, a similar operational effect can be obtained.

Claims: A rotary valve for an automatic transmission, said rotary valve comprising a spool (7) rotatably received within a valve housing (1) and driven by an actuator (6) for selectively supplying hydraulic pressure from a hydraulic pressure source (S) to each of a plurality of frictionally engaging elements (C₁-C₅) of said automatic transmission through said spool, wherein said rotary valve (V) includes a central oil passage (12₀) formed in said spool and extending along an axis of rotation of said spool, radiate oil passages (12₁-12₅) formed in said spool and spaced axially along and radially from said central oil passage, and an oil supply port (13) opened into said central oil passage (12₀), characterized in that said oil supply port (13) opens into an axial end of said central oil passage (12₀), and that only radiate oil passages (12₁-12₅) are formed in said spool, are spaced axially along and extend symmetrically and radially from said central oil passage. A rotary valve for an automatic transmission according to claim 1, further including a thrust bearing (10) mounted between said spool (7) and said valve housing (1) for receiving loads axially acting on said spool. A rotary valve for an automatic transmission according to claim 1, further including a feed pipe (14) connected to said hydraulic pressure source (S) and connected to said central oil passage (12₀). A rotary valve for an automatic transmission according to claim 3, further including a bushing (19) mounted between an outer periphery of said feed pipe (14) and an inner periphery of said central oil passage (12₀) in said spool (7). A rotary valve for an automatic transmission according to claim 1, wherein said rotary valve (V) includes a drain port (28b₁-28b₅) communicatable with selected one of said frictionally engaging elements of said automatic transmission when said spool (7) is rotated from a predetermined position for permitting the supply of said hydraulic pressure to said selected frictionally engaging element to a position for permitting the supply of the hydraulic pressure to another of said frictional engaging elements for a higher gear shift, and a drain port (28a₁-28a₅) communicatable with said selected frictionally engaging element, when said spool (7) is rotated from said predetermined position to a position for permitting the supply of the hydraulic pressure to another of said frictionally engaging elements for a lower gear shift, said drain ports (28a₁-28a₅; 28b₁-28b₅) being provided independently of said supply of hydraulic pressure.

Inventors: FURUKAWA HIDEO C O KABUSHIKI K, HATAKEYAMA KAZUMA C O KABUSHIK, KIMURA KOICHI C O KABUSHIKI KA, FURUKAWA, HIDEO, C/O KABUSHIKI KAISHA HONDA, HATAKEYAMA, KAZUMA, C/O KABUSHIKI KAISHA HONDA, KIMURA, KOICHI, C/O KABUSHIKI KAISHA HONDA
Applicants: HONDA MOTOR CO LTD, HONDA GIKEN KOGYO KABUSHIKI KAISHA
Application year: 1992
Main classification: F16H59
IPC codes: F16H61