JP4887940B2 - Automatic transmission - Google Patents

Description

  The present invention relates to an automatic transmission.

  In an automatic transmission, particularly an automobile automatic transmission, a multi-stage transmission gear mechanism is configured by a planetary gear mechanism, and the planetary gear mechanism is housed in a transmission casing and a predetermined rotating member in the planetary gear mechanism is shifted. Engagement with the machine casing is performed. For example, as shown in Patent Document 1, various brakes, clutches, and even one-way clutches are used for changing the gear position. For example, a specific brake such as a lowry bus brake is used to configure the first speed. And a specific one-way clutch are incorporated as one set. In this case, the specific brake and the specific one-way clutch that are set as one set serve as an engagement member for engaging the predetermined rotation member with the transmission casing, but in order to cope with a large transmission torque, Generally, it is annularly arranged on the outer periphery of the planetary gear mechanism.

  There are various one-way clutches, but as shown in Patent Document 2, there is a so-called plate-like coupling that can secure a large transmission torque. The plate-like coupling forms a pocket portion on one facing surface of the two opposing first coupling plate and second coupling plate, while forming a notch portion on the other facing surface, The struts swinging around one end in the circumferential direction are housed in a tiltable manner, and the struts are urged toward the standing position by a spring member so that the struts in the standing position are engaged with the notches. By doing so, the relative rotation toward the other end in the circumferential direction is restricted (locked). And in patent document 2, although what uses a plate-shaped coupling as said specific one-way clutch is disclosed in the automatic transmission, this plate-shaped coupling is arrange | positioned at the outer periphery of the planetary gear mechanism. .

Further, in Patent Document 3, as the strut, a first strut having a rocking fulcrum at one end in the circumferential direction and a second strut having a rocking fulcrum at the other end in the circumferential direction are provided. One slide plate having a hole portion and a non-hole portion is provided between the two struts, and by changing the rotation position (slide position) of this slide plate, only one of both struts is set to the standing position. Disclosed is a switch between a direction lock state, an other direction lock state in which only the other is in an upright position, and a neutral state in which both struts are in a lying position (a state in which relative rotation in both directions is allowed). ing. However, in the thing of patent document 3, since there is one slide plate, it is difficult to obtain a two-way locked state in which both struts are in the standing position.
JP 2003-83439 A JP-T-2001-526366 JP-T-2002-514292

  As shown in Patent Document 2, when a plate-like coupling is used as an engaging member for engaging a predetermined rotating member in a planetary gear mechanism with a transmission casing, the transmission torque received by the plate-like coupling is considerable. Become bigger. For this reason, the problem is how to make the plate-like coupling stable. That is, the first coupling plate and the second coupling plate, which are arranged opposite to each other in the plate-like coupling and are rotated relative to each other, transmit torque only between the one opposed surfaces, so that a large transmission torque can be stabilized. In order to make it a structure that accepts it, some countermeasure is desired.

  The present invention has been made in consideration of the above circumstances, and its purpose is to use a plate-like coupling as an engaging member for engaging a predetermined rotating member in a planetary gear mechanism with a transmission casing. Another object of the present invention is to provide an automatic transmission that can stably receive a large transmission torque.

In order to achieve the above object, the following solution is adopted in the present invention. That is, as described in claim 1 in the claims,
An automatic transmission in which a planetary gear mechanism constituting a multi-stage transmission gear mechanism is housed in a transmission casing, and a predetermined rotating member in the planetary gear mechanism is engaged with the transmission casing via a plate-like coupling. In
The plate-like coupling is
An annular first coupling plate integral with the transmission casing;
An annular one-surface-side second coupling plate that is integrated with the predetermined rotating member and is arranged to face one surface of the first coupling plate;
An annular second surface side second coupling plate that is integrated with the predetermined rotating member and is disposed to face the other surface side of the first coupling plate;
A pocket portion provided on one of the opposing surfaces of the opposing surface of the first coupling plate and the one-surface-side second coupling plate and the opposing surface of the first coupling plate and the other-surface-side second coupling plate. And a notch provided on the other of the opposing surfaces;
Each of the second pockets is housed in the pockets and is tilted up and down by swinging around one end in the circumferential direction of the central axis, and is engaged with the notch in the standing state. A strut that restricts rotation of the coupling plate to the other side in the circumferential direction;
A spring member housed in each of the pocket portions and biasing the struts toward the standing position;
Equipped with a,
The predetermined rotating member includes a first portion extending along one surface side of the first coupling plate, a second portion extending along the other surface side of the first coupling plate, and the first portion and the second portion. An annular connecting member having a substantially U-shaped cross section composed of a third portion connecting the inner peripheral side end portions to each other is integrated.
Among the connecting members, the first portion includes the first surface side second coupling plate, and the second portion includes the other surface side second coupling plate.
It is like that.

  According to the above solution, the plate-like coupling generates a large transmission torque by sandwiching one first coupling plate fixed to the transmission casing between the two second coupling plates that are rotated together with a predetermined rotating member. Since it is designed to receive a large transmission torque on both the one surface side and the other surface side of the first coupling plate, when receiving a large transmission torque only on one surface side of the first coupling plate. In comparison, a stable engagement state can be obtained.

Further, the predetermined rotating member includes a first portion extending along one surface side of the first coupling plate, a second portion extending along the other surface side of the first coupling plate, the first portion and the first portion. An annular connecting member having a substantially U-shaped cross section composed of a third portion connecting the inner peripheral side end portions with the two portions is integrated, and the first portion of the connecting members is on the one surface side. with a second coupling plate composed, since the other side a second coupling plate in said second portion are as, and is configured, the two second coupling plate, substantially U-shaped cross-section The connecting member can be used for simple configuration, and the two second coupling plates can be simultaneously fixed to the predetermined rotating member by fixing one connecting member to the predetermined rotating member.

A preferred mode based on the above solution is as described in claim 2 and the following claims. That is,
The first coupling plate and the second coupling plates are arranged in series in the central axis direction with respect to the predetermined rotating member,
In the direction orthogonal to the central axis, the position of the outer peripheral edge of each second coupling plate is substantially coincident with the position of the outer peripheral edge of the predetermined rotating member.
(Corresponding to claim 2 ). In this case, the transmission casing can be made sufficiently small in the radial direction at least in the portion where the conventional one-way clutch is provided. In addition, since the axial dimension of the plate-like coupling can be made sufficiently small, the space in the central axis direction of the existing planetary gear mechanism can be incorporated as it is, and the planetary gear mechanism can be incorporated. It is also possible to avoid lengthening the length in the direction of the central axis. Furthermore, the outer diameter of the second coupling plate 2 is ensured as large as possible within a range not exceeding the outer diameter of the predetermined rotating member, which is preferable for receiving a large transmission torque.

Between each of the first coupling plate and each of the second coupling plates, a slide plate that is annular around the central axis and slidable around the central axis is disposed.
Each slide plate has a hole portion and a non-hole portion, and is set to allow the strut to be in an upright position when the hole portion is positioned on the strut;
Actuators for synchronizing and sliding the slide plates are provided,
(Corresponding to claim 3 ). In this case, the sliding state of each slide plate is synchronized and driven by the actuator, so that the engagement state of each second coupling plate with respect to the first coupling plate can be reliably made the same.

In order to achieve the above object, the following solution is adopted in the present invention. That is, as described in claim 4 in the claims,
An automatic transmission in which a planetary gear mechanism constituting a multi-stage transmission gear mechanism is housed in a transmission casing, and a predetermined rotating member in the planetary gear mechanism is engaged with the transmission casing via a plate-like coupling. In
The plate-like coupling is
An annular first coupling plate integral with the transmission casing;
An annular one-surface-side second coupling plate that is integrated with the predetermined rotating member and is arranged to face one surface of the first coupling plate;
An annular second surface side second coupling plate that is integrated with the predetermined rotating member and is disposed to face the other surface side of the first coupling plate;
A pocket portion provided on one of the opposing surfaces of the opposing surface of the first coupling plate and the one-surface-side second coupling plate and the opposing surface of the first coupling plate and the other-surface-side second coupling plate. And a notch provided on the other of the opposing surfaces;
Each of the second pockets is housed in the pockets and is tilted up and down by swinging around one end in the circumferential direction of the central axis, and is engaged with the notch in the standing state. A strut that restricts rotation of the coupling plate to the other side in the circumferential direction;
A spring member housed in each of the pocket portions and biasing the struts toward the standing position;
With
As the struts, in addition to the first strut being defeated caused by swung fulcrums first peripheral end portion of the central axis, brought down force to the second peripheral end portion of said central axis as a fulcrum A second strut is provided,
In addition to the first notch portion corresponding to the first strut as the notch portion, a second notch portion corresponding to the second strut is provided, and the rotation restriction of each second coupling plate by the first strut is provided. Direction and the rotation restricting direction of each second coupling plate by the second struts are set to be opposite to each other,
Between the first coupling plate and each of the second coupling plates, a first slide plate and a second slide plate that are annular around the central axis and are slidable around the central axis are disposed.
Each of the first slide plate and each second slide plate has a hole portion and a non-hole portion, and is set so that only the strut in which each hole portion of each slide plate is positioned is set to the standing position. And
An actuator that drives the first slide plates in synchronization with each other and an actuator that drives the second slide plates in synchronization with each other are provided.
It is like that.
According to the above solution , the first and second struts are individually switched between the standing position and the lying position by using a total of four slide plates in which two slide plates are arranged for each facing surface. In addition to functioning as a simple one-way clutch, both the first and second struts are in the standing position, and the bi-directionally locked state in which the rotation of the predetermined rotating member in both directions is restricted (locked) is also achieved. Can do. This allows the plate-like coupling to function as a brake.

In accordance with the change in the slide position of each slide plate, at least the first strut and the second strut are each in the standing position, and the bi-directionally locked state in which the rotation of each second coupling plate is restricted in both directions; A unidirectional lock state in which the first strut is in a standing position and the second strut is in a lying position, and each second coupling plate is restricted from rotating in one direction, and the first strut and the second strut are A neutral state in which each of the second coupling plates is allowed to rotate in both directions and is allowed to rotate in both directions is provided (corresponding to claim 5 ). In this case, it is possible to completely achieve the function of the one-set body composed of a specific brake and a specific one-way clutch.

When the manually operated select lever is in the D range position that is an automatic shift command in forward travel, the one-way locked state is set to constitute a predetermined shift stage,
When the manually operated select lever is in the manual mode position for issuing a shift speed change command during forward travel every time the manual operation is performed, the two-way lock state is set to constitute the predetermined shift speed. ing,
(Corresponding to claim 6 ). In this case, for example, the function of the low reverse brake in Patent Document 1 can be obtained. In particular, in the manual mode, the engine brake can be obtained while ensuring a shift with a direct feeling in the bidirectionally locked state.

When the select lever selects reverse travel, the two-way locked state is set and a reverse shift stage is configured (corresponding to claim 7 ). In this case, for example, it is possible to obtain a function of obtaining a reverse gear using the low reverse brake of the automatic transmission in Patent Document 1.

At the time of power-off, the neutral state is set (corresponding to claim 8 ). In this case, it is preferable in terms of reducing rotational resistance when power transmission from the input shaft side to the output shaft side of the automatic transmission is not performed.

At the time of power-off, the bidirectional lock state is set (corresponding to claim 9 ). In this case, when power transmission from the input shaft side to the output shaft side of the automatic transmission is not performed, it is preferable for securing the engine brake.

The pocket portion, the strut, and the spring member are each provided on the first coupling plate (corresponding to claim 10 ). In this case, it is preferable for reducing the inertial mass of the predetermined rotating member to be rotated.

  According to the present invention, when a predetermined rotating member is engaged with a transmission casing using a plate-like coupling, a large transmission torque can be stably received.

  The automatic transmission 100 includes, as main components, a torque converter 120, two planetary gear mechanisms 130 and 140 as multi-stage transmission gear mechanisms driven by the output of the torque converter 120, and the planetary gear mechanisms 130 and 140. A plurality of friction elements 151 to 154 for switching the power transmission path and a pair of plate-like couplings PC1 and PC2 are provided. In the embodiment, as will be described later, the plate-like couplings PC1 and PC2 function both as a specific brake (low reverse brake) and a specific one-way clutch (reference numeral 55 in Patent Document 1). The low reverse brake shown and the one-way clutch shown by reference numeral 56 are performed).

  When the manually operated select lever (not shown) is in the D range position, automatic transmission between 1st to 4th speed is performed, and when the select lever selects the manual mode, the select lever is Each time a predetermined manual operation is performed, the gear is shifted up or down by one step, and the reverse speed can be realized when the select lever is at the R range position.

  The torque converter 120 includes a pump 122 fixed in a casing 121 connected to the engine output shaft 101, and a turbine 123 that is disposed so as to face the pump 122 and is driven by the pump 122 via hydraulic oil. A stator 125 interposed between the pump 122 and the turbine 123 and supported by the transmission casing 111 via a one-way clutch 124, and an engine output shaft provided between the casing 121 and the turbine 123. 101 and a lockup clutch 126 that directly connects the turbine 123 to the turbine 123. The rotation of the turbine 123 is output to the planetary gear mechanisms 130 and 140 via the turbine shaft 127. An oil pump 112 driven by the engine output shaft 101 via the casing 121 of the torque converter 120 is disposed on the opposite side of the torque converter 120.

  The planetary gear mechanisms 130 and 140 mesh with the sun gears 131 and 141, the plurality of pinions 132 and 142 that mesh with the sun gears 131 and 141, the pinion carriers 133 and 143 that support the pinions 132 and 142, and the pinions 132 and 142. Ring gears 134 and 144.

  A forward clutch 151 is provided between the turbine shaft 127 and the sun gear 131 of the first planetary gear mechanism 130, and a reverse clutch 152 is provided between the turbine shaft 127 and the sun gear 141 of the second planetary gear mechanism 140. A 3-4 clutch 153 is interposed between the second planetary gear mechanism 140 and the pinion carrier 143. The 2-4 brake 154 fixes the sun gear 141 of the second planetary gear mechanism 140. A ring gear 134 of the first planetary gear mechanism 130 and a pinion carrier 143 of the second planetary gear mechanism 140 are connected, and between these and the transmission casing 111, plate-like couplings PC1 and PC2 (a low reverse brake and a one-way). Clutch) is arranged. The pinion carrier 133 of the first planetary gear mechanism 130 and the ring gear 144 of the second planetary gear mechanism 140 are coupled, and the output gear 113 is connected to them.

  The output gear 113 and the first intermediate gear 162 on the idle shaft 161 constituting the intermediate transmission mechanism 160 mesh with each other, and the second intermediate gear 161 on the idle shaft 161 and the input gear 170 of the differential device 170 mesh with each other. The rotation of the output gear 113 is input to the differential casing 172 of the differential device 170, and the left and right axles 173 and 174 are driven through the differential device 170.

  The 2-4 brake 154 includes a band brake. The 2-4 brake 154 has a fastening chamber and a release chamber. The brake 154 is fastened when the operating pressure is supplied only to the fastening chamber, and is not supplied to the fastening chamber and when the operating pressure is supplied to the release chamber. Is released when is supplied. The other friction elements 51 to 53 have a single hydraulic chamber and are fastened when operating pressure is supplied to the hydraulic chamber.

  FIG. 2 shows the relationship between the operating states of the friction elements 151 to 154 and the plate-like couplings PC1 and PC2 and the gear position. In FIG. 2, as will be understood from the description of the plate-like couplings PC1 and PC2, which will be described later, the bidirectional lock state corresponds to the engaged state of the low reverse brake, and the one-way locked state indicates that the one-way clutch is activated. Become.

Here, the aforementioned ring gear 134 is a predetermined rotating member in the present invention, and this ring gear 134 has a predetermined coupling to the transmission casing 111 via the plate-like couplings PC1 and PC2. State. FIG. 3 shows details of the plate-like couplings PC1 and PC2, and FIG. 3 will be described below. In FIG. 3, the central axis of the turbine shaft 127 that also serves as the central axis of the planetary gear mechanism is indicated by a symbol L.

  First, the transmission casing 111 has an annular vertical wall portion 180 that extends toward the central axis L and surrounds the central axis. The vertical wall portion 180 is located between the ring gear 134 and the output gear 113 on the side close to the output gear 113 in the central axis L direction. The inner peripheral portion of the vertical wall member 180 has a cylindrical portion 181 that extends along the predetermined axis L in a direction approaching the ring gear 134. The cylindrical portion 181 is centered on a predetermined axis L, and the outer periphery of the tip portion of the cylindrical portion 180 (the end portion close to the ring gear 134) is used as a predetermined rotating member via a first bearing 182. The ring gear 134 (the end portion on the vertical wall portion 180 side) is supported. Further, the inner peripheral portion of the cylindrical portion 181 supports the shaft portion of the output gear 113 via the second bearing 183.

  On the inner surface of the casing 111, the plate-like couplings PC1 and PC2 described above are disposed between the ring gear 134 and the vertical wall member 180. That is, the first coupling plate 1 made of an annular ring member having a relatively large thickness is fixed to the inner surface of the casing 111. The first coupling plate 1 has an annular shape centered on the central axis L, and is positioned between the ring gear 134 and the vertical wall member 180 so as to surround the outer periphery of the cylindrical portion 181. . The first coupling plate 1 is used commonly for the plate-like couplings PC1 and PC2.

  A connecting member 185 having a generally U-shaped cross section is fixed from the end of the ring gear 134 on the vertical wall 180 side. The connecting member 185 includes a pair of second connecting plates 2 disposed so as to sandwich the first connecting plate 1 from the central axis L direction, and connecting portions that connect inner peripheral side ends of the second connecting plates 2. 186, and two divided members are integrated by a coupling plate 187. The first bearing 182 is disposed slightly offset from the plate-like couplings PC1 and PC2 on the side close to the ring gear 134 in the central axis L direction.

  Next, the details of the plate-like couplings PC1 and PC2 will be described with reference to FIG. 4 and subsequent figures. However, since the PC1 and the PC2 are configured in the same manner, attention is paid to one plate-like coupling PC1. Will be described. The pair of plate-like couplings PC1 and PC2 is provided by securing a stable structure by increasing the transmission torque and arranging the first coupling plate 1 in both directions. Is for etc.

  4 to 6, a first slide plate 11 and a second slide plate 12 are disposed between the first coupling plate 1 and the second coupling plate 2. Each of the slide plates 11 and 12 is formed in an annular shape centered on the central axis L (see FIGS. 7 and 8, the second coupling plate 2 is omitted in FIGS. 7 and 8). The respective coupling plates 1 and 2 are arranged to face each other so as to be relatively rotatable with a small space therebetween, and the two slide plates 11 and 12 are disposed between the two coupling plates 1 and 2. The arrangement relationship of the members 1, 2, 11, and 12 will be described with reference to FIG. 4, for example, from one end side (lower side in FIG. 4) to the other end side (upper side in FIG. 4). The first coupling plate 1, the first slide plate 11, the second slide plate 12, and the second coupling plate 2 are provided. The central axis L extends in the direction perpendicular to the paper surface in FIG.

  Each of the coupling plates 1 and 2 is formed to be thick so as to increase rigidity in terms of transmitting power to each other. Since the slide plates 11 and 12 do not directly participate in power transmission, they are formed thin. Each of the members 1, 2, 11, and 12 is formed of a metal such as an iron-based metal. Of course, the first coupling plate 1 is always fixed (integrated with the transmission casing 111), and the second coupling plate 2 is a rotating member. The outer peripheral edge portion of each second coupling plate 2 is set so as to be substantially coincident with the outer peripheral edge portion of the ring gear 134 as a predetermined rotating member in the radial direction of the central axis L. The second coupling plate 2 is arranged on the outer periphery of the ring gear 134 by the serial arrangement of the coupling plates 1 and 2 with respect to the ring gear 134 and the structure in which the second coupling plates 2 do not protrude greatly outward in the radial direction of the ring gear 134. The transmission casing 111 can be made sufficiently small in the radial direction as compared with the case where it is arranged. Further, by setting the outer peripheral edge portion of the second coupling plate 2 substantially coincident with the outer peripheral edge portion of the ring gear 134, the outer diameter of the second coupling plate 2 is ensured as much as possible and receives a large transmission torque. Preferred above.

  Two first pocket portions (concave portions) 21 are formed on the facing surface of the first coupling plate 1, that is, the surface facing the second coupling plate 2 with a 180 ° interval in the circumferential direction. Two second pocket portions 22 are formed at intervals of 180 degrees in the direction (see also FIGS. 7 and 8). And between the two 1st pocket parts 21, it sets so that the 2nd pocket part 22 may be located, and each pocket part 21 and 22 which adjoins is arrange | positioned by the 90 degree space | interval in the circumferential direction. The shapes and sizes of the pocket portions 21 and 22 are set to be the same.

  On the opposing surface of the second coupling plate 2, that is, the surface facing the first coupling plate 1, two first notch portions 31 are formed corresponding to the two first pocket portions 21 described above, Two second notch portions 32 are formed corresponding to the two second pocket portions 22. The two first notch portions 31 are arranged at an interval of 180 degrees in the circumferential direction, the two second notch portions 32 are arranged at an interval of 180 in the circumferential direction, and the circumferential interval between adjacent notch portions 31 and 32 is 90. It is considered a degree. The notches 31 and 32 are set so as to be symmetrical in the circumferential direction of the central axis L.

  The slide plates 11 and 12 are set to have the same shape (joint shape). More specifically, the first slide plate 11 is formed with a total of four hole portions 11a spaced apart in the circumferential direction (non-hole portions are indicated by reference numerals 11b), and similarly to the second slide plate 12 Also, a total of four hole portions 12a (non-hole portion portions are indicated by reference numerals 12b) are formed at intervals in the circumferential direction. The first slide plate 11 and the second slide plate 12 are completely aligned (aligned) with the hole portions 11a and 12a in a predetermined overlapping state. Each hole part 11a, 12a is formed in the circular arc shape centering on the central axis L. As shown in FIG. The hole portions 11a and 12a have substantially the same width (length in the direction perpendicular to the central axis L) as the width of the pocket portions 21 and 22, but the circumferential direction of the hole portions 11a and 12a. The length is set to be sufficiently longer than the circumferential lengths of the pocket portions 21 and 22. In addition, in FIG. 7 etc., in order to clearly show the position of the hidden hole portion 11a of the first slide plate 11 and the like, there is also a portion drawn slightly shifted from the second slide plate 12, but in actuality, The first slide plate 11 and the second slide plate 12 are set to a completely congruent shape.

  A first strut 41 is housed in the first pocket portion 21 so as to be able to be tilted up and down. The first strut 21 can be swung about one end in the circumferential direction as a fulcrum, and in accordance with the swing, the first strut 21 is moved from the lying position stored in the first pocket portion 21 and from the first pocket portion 21 to the first strut 21. The upright position which protrudes greatly toward the 2 coupling plate 2 side can be taken. The first strut 41 is configured to be excellent in rigidity with, for example, an iron-based metal in terms of transmitting torque.

  Similarly, a second strut 42 is housed in the second pocket portion 22 so that it can be tilted up and down. The second strut 21 can be swung with the other end in the circumferential direction as a fulcrum. According to the swing, the second strut 21 is moved from the lying position stored in the second pocket portion 22 and from the second pocket portion 22. An upright position that greatly protrudes toward the second coupling plate 2 can be taken. The second struts 42 are for rotation locking in the opposite direction with respect to the first struts 41. For this reason, the swing fulcrum is on the opposite side in the circumferential direction with respect to the first struts 41. Is set. The second strut 42 is configured to be excellent in rigidity, for example, by an iron-based metal in terms of performing torque transmission.

  In the first pocket portion 21, a first spring member 51 that biases the first strut 41 toward the standing position is disposed on the back side of the first strut 41 (the side opposite to the second coupling plate 2). Yes. Similarly, a second spring member 52 that urges the second strut 42 toward the upright position is disposed in the second pocket portion 22 on the back side of the second strut 42 (the side opposite to the second coupling plate 2). It is installed. The spring members 51 and 52 have the same shape and size, and in the embodiment, are constituted by coil springs. More specifically, in a state where the axis of the coil spring is extended in the radial direction of the first coupling plate 1, one end 51 a (52 a) extending elongated is brought into contact with the back side of the strut 41 (42), and the other end The part 51b (52b) is in contact with the bottom side of the pocket part 21 (22). When the strut 41 (42) is in the lying position shown in FIGS. 5 and 6, the spring member 51 (52) has one end 51a (52a) and the other end as compared to the standing position shown in FIG. The angle formed by 51b (52b) is reduced. A storage recess 21a (22a) for storing the spring member 51 (52) is formed on the bottom surface of the pocket portion 21 (22), and the spring member 51 ( 52) is set so as not to be extremely greatly deformed, that is, the angle formed between the one end portions 51a and 51b (52a and 52b) is not excessively small.

  Each of the struts 41 and 42 is in a posture in which the struts 41 and 42 are inclined at, for example, about 30 degrees to 40 degrees with respect to the lying position, in the rotational direction between the first coupling plate 1 and the second coupling plate 2. Torque is transmitted. And the front-end | tip part (end part on the opposite side to the rocking | fulcrum fulcrum side edge part) of the struts 41 and 42 in a standing position is the inclined surface by which the inclination angle was set comparatively large among the above-mentioned notch parts 31 and 32. The end portions of the struts 41 and 42 on the swing fulcrum side are also in surface contact with the circumferential end surfaces of the pocket portions 21 and 22.

  As shown in FIG. 7, a protrusion 11c extending outward in the circumferential direction is formed on the outer edge of the first slide plate 11, and the first actuator 61 is coupled to the protrusion 11c. Similarly, a protrusion 12c extending outward in the circumferential direction is formed on the outer edge of the second slide plate 12, and the second actuator 62 is connected to the protrusion 12c. The slide plates 11 and 12 are slid independently (rotated around the central axis L) by the actuators 61 and 62 independently of each other.

  Next, the effect | action of the above structures is demonstrated, referring FIGS. 7-11. 7 to 11 show a state in which the second coupling plate 2 is removed so that the movements of the struts 41 and 42 are clear. Moreover, in the following description, the one side rotation direction around the central axis L of the second coupling plate 2 will be described as the normal rotation direction, and the other direction rotation direction will be described as the reverse rotation direction.

  First, the position shown in FIGS. 7 and 8 is a two-way locked state in which the second coupling plate 2 is restricted from rotating in both directions around the central axis L with respect to the first coupling plate 1. That is, the projections 11c and 12c of the slide plates 11 and 12 are set to the reference position α where the projections 11c and 12c match each other, and at this time, the hole portions 11a and 12a of the slide plates 11 and 12 with respect to the pockets 21 and 22, respectively. Are perfectly aligned.

  7 and 8, the first strut 41 in the upright position passes through the hole portions 11 a and 12 a of the slide plates 11 and 12, and the first notch portion 31 of the second coupling plate 2. Engage (see FIG. 4), and the function of locking the rotation of the second coupling plate 2 in the forward rotation direction is performed based on the setting of the standing direction. Further, the second strut 42 in the standing position passes through the hole portions 11a and 12a of the slide plates 11 and 12, and engages with the second notch portion 32 of the second coupling plate 2 (see FIG. 4). From the setting of the standing direction, the function of locking the rotation of the second coupling plate 2 in the reverse direction is performed. In such a bi-directionally locked state, of the end portions in the circumferential direction of the hole portions 11a, 12a, the struts 41, 42 that are in the standing position are close to the struts 41, 42 on the side close to the swinging fulcrum. The circumferential end on the side far from the swing fulcrum is located far away from the struts 41, 42.

  FIG. 9 shows a state in which only the first slide plate 11 is slid (rotated) slightly in the forward rotation direction from the reference position α from the bidirectionally locked state shown in FIGS. 7 and 8. In this state of FIG. Only the second strut 42 is set to the lying position stored in the second pocket portion 22 as shown in FIG. As a result, the first strut 41 is brought into a normal rotation direction (one direction) locked state in which the rotation of the second coupling plate 2 in the normal rotation direction is restricted.

  FIG. 10 shows a state in which only the first slide plate 11 is slid (turned) slightly in the reverse direction from the reference position α from the bidirectionally locked state shown in FIGS. 7 and 8. In this state of FIG. Only one strut 41 is set to the lying position stored in the first pocket portion 21 as shown in FIG. As a result, the second strut 42 is brought into the reverse direction (other direction) locked state in which the rotation of the second coupling plate 2 in the reverse direction is restricted.

  7 and 8, the first slide plate 11 is slightly slid (rotated) in the forward rotation direction from the reference position α, and the second slide plate 12 is slightly slid in the reverse rotation direction from the reference position α. FIG. 11 shows the state of (rotation). In the state shown in FIG. 11, both struts 41 and 42 are set to the lying positions stored in the pocket portions 41 or 42. Thereby, the rotation of the second coupling plate 2 is not restricted at all by the struts 41 and 42, that is, the neutral state is established in which the second coupling plate 2 can rotate in both the forward direction and the reverse direction. In the neutral state, the first strut 41 is set to the fall position by the second slide plate 12, and the second strut 42 is set to the fall position by the first slide plate 11.

In the example shown in FIGS. 8 to 11 described above, the position of the first slide plate 41 is changed between a total of three positions including the reference position α, and the second slide plate 42 includes a total of 2 including the reference position α. The position is changed between the two positions, and the combination of the positions of the slide plates 11 and 12 allows both the locked state, the forward direction locked state, the reverse direction locked state, and the rotation in both directions as described above. A total of four states including the neutral state to be performed are arbitrarily selected. The state change between the four states is performed by individually driving the slide plates 41 and 42 by the two actuators 61 and 62. In addition, since the 1st slide plate 11 and the 2nd slide plate are set to the congruent shape, in order to change between the four states mentioned above, the movement of the 1st slide plate 11 and the 2nd slide plate 12 is carried out. Can also be obtained by reversing the above description.

  FIGS. 12 and 13 show another embodiment of the present invention. The same components as those in the above embodiment are given the same reference numerals, and redundant description thereof is omitted. In this embodiment, the strut 41 (the same applies to 42) is held on the first coupling plate 1 so as to be swingable about the pin 71. Oscillation using the pin 71 is preferable for smoothly oscillating the first strut 41. The first strut 41 can be relatively displaced in the longitudinal direction with respect to the pin 71 so that the first strut 41 reliably contacts the circumferential end surface of the first pocket portion 21 when in the standing position. (The transmission torque is not applied to the pin 71). In the present embodiment, a leaf spring is used as the first spring member 51 (the same applies to 52) instead of the coil spring. In addition, as the spring member 51 (the same applies to 52), the type of the spring member 51 and the arrangement method thereof may be appropriately selected, such as using the spring force in the axial direction of the coil spring.

  FIGS. 14 to 17 show still another embodiment of the present invention. Each of the slide plates 11 and 12 is changed between two positions so that the four states described above can be taken. Is. That is, FIGS. 14 to 17 correspond to FIG. 7 respectively. FIG. 14 shows the two-way locked state (corresponding to FIG. 7, but the positions of the protrusions 11c and 12c are slightly different from those in FIG. 7).

  The state shown in FIG. 15 is a state in which the first slide plate 41 is slightly slid (rotated) in the normal rotation direction from the two-way locked state shown in FIG. 14 so that the protrusion 11c matches the protrusion 12c. In the state of FIG. 15, the forward rotation direction (one direction) locked state in which the rotation of the second coupling plate 2 in the forward rotation direction is locked.

  The state shown in FIG. 16 is a state in which the second slide plate 22 is slightly slid (rotated) in the reverse direction from the state shown in FIG. 14 so that the protrusion 12a matches the protrusion 11a. The state shown in FIG. 16 is a locked state in the reverse rotation direction (the other direction).

  From the state of FIG. 14, the first slide plate 11 is slightly slid (rotated) in the forward direction and the second slide plate 12 is slightly slid (rotated) in the reverse direction, that is, both the protrusions 11 c and The state in which 12c is replaced from the state of FIG. 14 is the state of FIG. The state of FIG. 17 is a neutral state in which rotation in both directions is allowed.

  FIG. 18 shows an example of an actuator that changes the position of each slide plate 11, 12 between two positions in the embodiment of FIGS. 14 to 17. In the example of FIG. 18, the actuator is hydraulic. That is, 90 is a valve body disposed at the bottom of the transmission casing 111, and two cylinder portions 91 a and 91 b are formed in the valve body 90. A first piston 92a is disposed in the cylinder portion 91a so as to be able to reciprocate, and a second piston 92b is disposed in the cylinder portion 91b so as to be capable of reciprocating.

  The first piston 92a is urged in one direction by a spring 93a. Similarly, the second piston 92b is urged in the other direction by a spring 93b. An oil chamber 94a defined in the cylinder portion 91a by the piston 92a is connected to the pump 96 via an electromagnetic switching valve 95a. Similarly, an oil chamber 94b defined in the cylinder portion 91b by the piston 92b is connected to the pump 96 via an electromagnetic switching valve 95b. Reference numeral 97 denotes an accumulator.

  When the oil chamber 94a is connected to the pump 96 side by the switching valve 95a, the first piston 92a is moved against the spring 93a and moved to the stroke end in the other direction. When the oil chamber 94a is drained by the switching valve 95a, the first piston 92a is returned to the one-way stroke end in FIG. 18 by the spring 93a. From such a first piston 92a, an extension portion 98a extends to the outside of the valve body 90, and is formed on the protrusion portion 11c (of the first slide plate 11 with respect to a pin 99a provided on the extension portion 98a. Are fitted and connected. The first piston 92a is repositioned between two positions. Since each of the two positions is a stroke end, the positioning is performed with extremely high accuracy. Positioning is also performed with high accuracy.

  The second piston 92b is configured in the same manner as the first piston 92a. Therefore, by using the sign of “b” instead of the sign of “a” used for the first piston 92a, an overlapping description thereof is given. Is omitted. Of course, the second piston 92 b is connected to the second slide plate 12. In the example of FIG. 15, the first piston 92 a constitutes the first actuator 61, the second piston 92 b constitutes the second actuator 62, and the valve body 90 is a common body for the first and second actuators. It is used as.

  The two pistons 92a are simultaneously driven to slide the two second coupling plates 11, the two pistons 92b are simultaneously driven to slide the two coupling plates 12, and the two pistons 92a and 92b are driven synchronously. As a result, the two coupling plates 2 arranged with the one first coupling plate 1 interposed therebetween are brought into the same engagement state in synchronism with the first coupling plate 1 (that is, the transmission casing 111). The one plate-like coupling PC1 and the second plate-like coupling PC2 are always in the same state). Such synchronous driving is the same in the example of FIG. 19 described below.

  FIG. 19 shows a modification of FIG. 18, in which only one piston 92 is slidably fitted in one cylinder 91. Two oil chambers 94a and 94b are defined on each end side of the piston 92, and springs 93a and 93b are disposed in the oil chambers 94a and 94b. In this embodiment, when each oil chamber 94a, 94b is drained, the piston 92 is set to the neutral position. When hydraulic pressure is supplied to one oil chamber 94a and the other oil chamber 94b is drained, the piston 92 is displaced to the right in the drawing to the right stroke end position. On the contrary, when the oil pressure is supplied to the oil chamber 94b and the oil chamber 94a is drained, the piston 92 is displaced leftward in the drawing to reach the left stroke end position. In this way, the piston 92 can be switched between three positions. For example, in the embodiment shown in FIGS. 8 to 11, the piston 92 can be used when the position of the first slide plate 11 is changed at three positions. .

  Although the embodiment has been described above, the present invention is not limited to the embodiment, and can be appropriately changed within the scope described in the scope of claims. For example, the invention includes the following cases. . You may arrange | position the pocket parts 21 and 22, ie, the struts 41 and 42, and the spring members 51 and 52 in the 2nd coupling plate 2 side. The actuator is commonly used for two slide plates, and this one actuator and the two slide plates 11 and 12 are connected via a separate connecting mechanism, and the two slide plates 11 and 12 are shown in FIG. You may make it set so that it may become the motion of 8-11 (or the motion of FIGS. 14-17). Instead of sliding (turning) the slide plates 11 and 12 around the central axis L, for example, the slide plates 11 and 12 can be slid in a direction orthogonal to the central axis L, for example. The actuators 61 and 62 are not limited to hydraulic types, but may be appropriate types such as electric types. The number of the first pocket portion 21 (the same applies to the second pocket portion 22), that is, the first strut 41 or the like (the same applies to the second strut 42 or the like) may be one or three or more. The number of the pocket portions 21 and the second pocket portions 22 may be different from each other (particularly suitable when there is a difference in the magnitude of torque transmission in the rotation direction).

  The plate-like couplings PC1 and PC2 may have a function of only a one-way clutch (for example, the function of the one-way clutch 56 in Patent Document 1, and in this case, only a one-way lock function may be provided. 11 and 12 can be made unnecessary) or may have a function of only a brake (for example, the function of the low reverse brake 55 in Patent Document 1, in this case, the two-way locked state and the neutral state are Just get it). The plate-like couplings PC1 and PC2 may be selectively obtained in two engagement states of a one-way lock state and an other-direction lock state (predetermining a predetermined shift stage configuration and engine brake), and one-way. Two engagement states, a locked state and a neutral state, may be selectively obtained (predetermined shift speed configuration and rotational resistance reduction during power-off), and only a bidirectional lock state is obtained (predetermined) The engagement state to be obtained can be selected as appropriate. Depending on the type of engagement state to be obtained, the presence or absence of the slide plate and the number of slide plates can be appropriately varied. That's fine. As the planetary gear mechanism as the multi-speed gear mechanism, an appropriate type can be adopted. Of course, the object of the present invention is not limited to what is explicitly stated, but also implicitly includes providing what is substantially preferred or expressed as an advantage.

The skeleton figure which shows an example of the automatic transmission with which this invention is applied. The figure which shows the fastening relationship of the gear stage and friction element etc. of the automatic transmission shown in FIG. The principal part sectional drawing which shows the detail of a plate-shaped coupling part among FIG. FIG. 9 is a cross-sectional view corresponding to the line X1-X1 in FIG. The principal part sectional drawing which shows the state from which the 2nd strut was made into the fall position from the state of FIG. FIG. 5 is a cross-sectional view showing a state in which only the first strut is in a lying position from the state of FIG. 4. The front view when it sees from the 2nd coupling plate side in the state which removed the 2nd coupling plate. FIG. 9 is a perspective view of FIG. 7 showing a bidirectional lock state. The perspective view corresponding to FIG. 8 which shows a normal rotation direction locked state. The perspective view corresponding to FIG. 8 which shows a reverse rotation direction locked state. FIG. 9 is a perspective view corresponding to FIG. 8, showing a neutral state in which rotation in both directions is allowed. The principal part sectional view showing another embodiment of the present invention. The perspective view of the leaf | plate spring used for FIG. The front view corresponding to FIG. 7 which shows another embodiment of this invention, and shows a bidirectional | two-way lock state. The front view corresponding to FIG. 14 which shows a normal rotation direction locked state. The front view corresponding to FIG. 14 which shows a reverse direction locked state. The front view corresponding to FIG. 14 which shows the neutral state in which rotation of both directions was accept | permitted. The cross-sectional systematic diagram which shows an example of the actuator for changing the position of each slide plate between two positions. The cross-sectional systematic diagram which shows an example of the actuator for changing the position of each slide plate between three positions.

1: 1st coupling plate 2: 2nd coupling plate 11: 1st slide plate 11a: Hole part 11b: Non-hole part 11c: Protrusion part (connection part to an actuator)
12: 2nd slide plate 12a: Hole part 11b: Non-hole part 11c: Protrusion part (connection part to an actuator)
21: 1st pocket part 22: 2nd pocket part 31: 1st notch part 32: 2nd notch part 41: 1st strut 42: 2nd strut 51: 1st spring member 52: 2nd spring member 61: 1st Actuator 62: Second actuator 90: Valve body 92: Piston 92a: First piston (first actuator)
92b: second piston (second actuator)
93a: Spring 93b: Spring 95a: Switching valve 95b: Switching valve 96: Pump 100: Automatic transmission 111: Transmission casing 130, 140: Planetary gear mechanism 134: Ring gear (predetermined rotating member)

Claims (10)

An automatic transmission in which a planetary gear mechanism constituting a multi-stage transmission gear mechanism is housed in a transmission casing, and a predetermined rotating member in the planetary gear mechanism is engaged with the transmission casing via a plate-like coupling. In
The plate-like coupling is
An annular first coupling plate integral with the transmission casing;
An annular one-surface-side second coupling plate that is integrated with the predetermined rotating member and is arranged to face one surface of the first coupling plate;
An annular second surface side second coupling plate that is integrated with the predetermined rotating member and is disposed to face the other surface side of the first coupling plate;
A pocket portion provided on one of the opposing surfaces of the opposing surface of the first coupling plate and the one-surface-side second coupling plate and the opposing surface of the first coupling plate and the other-surface-side second coupling plate. And a notch provided on the other of the opposing surfaces;
Each of the second pockets is housed in the pockets and is tilted up and down by swinging around one end in the circumferential direction of the central axis, and is engaged with the notch in the standing state. A strut that restricts rotation of the coupling plate to the other side in the circumferential direction;
A spring member housed in each of the pocket portions and biasing the struts toward the standing position;
Equipped with a,
The predetermined rotating member includes a first portion extending along one surface side of the first coupling plate, a second portion extending along the other surface side of the first coupling plate, and the first portion and the second portion. An annular connecting member having a substantially U-shaped cross section composed of a third portion connecting the inner peripheral side end portions to each other is integrated.
Among the connecting members, the first portion includes the first surface side second coupling plate, and the second portion includes the other surface side second coupling plate.
An automatic transmission characterized by that. In claim 1,
The first coupling plate and the second coupling plates are arranged in series in the central axis direction with respect to the predetermined rotating member,
In the direction orthogonal to the central axis, the position of the outer peripheral edge of each second coupling plate is substantially coincident with the position of the outer peripheral edge of the predetermined rotating member.
An automatic transmission characterized by that. In claim 1 or 2 ,
Between each of the first coupling plate and each of the second coupling plates, a slide plate that is annular around the central axis and slidable around the central axis is disposed.
Each slide plate has a hole portion and a non-hole portion, and is set to allow the strut to be in an upright position when the hole portion is positioned on the strut;
Actuators for synchronizing and sliding the slide plates are provided,
An automatic transmission characterized by that. An automatic transmission in which a planetary gear mechanism constituting a multi-stage transmission gear mechanism is housed in a transmission casing, and a predetermined rotating member in the planetary gear mechanism is engaged with the transmission casing via a plate-like coupling. In
The plate-like coupling is
An annular first coupling plate integral with the transmission casing;
An annular one-surface-side second coupling plate that is integrated with the predetermined rotating member and is arranged to face one surface of the first coupling plate;
An annular second surface side second coupling plate that is integrated with the predetermined rotating member and is disposed to face the other surface side of the first coupling plate;
A pocket portion provided on one of the opposing surfaces of the opposing surface of the first coupling plate and the one-surface-side second coupling plate and the opposing surface of the first coupling plate and the other-surface-side second coupling plate. And a notch provided on the other of the opposing surfaces;
Each of the second pockets is housed in the pockets and is tilted up and down by swinging around one end in the circumferential direction of the central axis, and is engaged with the notch in the standing state. A strut that restricts rotation of the coupling plate to the other side in the circumferential direction;
A spring member housed in each of the pocket portions and biasing the struts toward the standing position;
With
As the struts, in addition to the first strut being defeated caused by swung fulcrums first peripheral end portion of the central axis, brought down force to the second peripheral end portion of said central axis as a fulcrum A second strut is provided,
In addition to the first notch portion corresponding to the first strut as the notch portion, a second notch portion corresponding to the second strut is provided, and the rotation restriction of each second coupling plate by the first strut is provided. Direction and the rotation restricting direction of each second coupling plate by the second struts are set to be opposite to each other,
Between the first coupling plate and each of the second coupling plates, a first slide plate and a second slide plate that are annular around the central axis and are slidable around the central axis are disposed.
Each of the first slide plate and each second slide plate has a hole portion and a non-hole portion, and is set so that only the strut in which each hole portion of each slide plate is positioned is set to the standing position. And
An actuator that drives the first slide plates in synchronization with each other and an actuator that drives the second slide plates in synchronization with each other are provided.
An automatic transmission characterized by that. In claim 4 ,
In accordance with the change in the slide position of each slide plate, at least the first strut and the second strut are each in the standing position, and the bi-directionally locked state in which the rotation of each second coupling plate is restricted in both directions; A unidirectional lock state in which the first strut is in a standing position and the second strut is in a lying position, and each second coupling plate is restricted from rotating in one direction, and the first strut and the second strut are A neutral state in which each of the second coupling plates is allowed to rotate in both directions by being in a lying position,
An automatic transmission characterized by that. In claim 5 ,
When the manually operated select lever is in the D range position that is an automatic shift command in forward travel, the one-way locked state is set to constitute a predetermined shift stage,
When the manually operated select lever is in the manual mode position for issuing a shift speed change command during forward travel every time the manual operation is performed, the two-way lock state is set to constitute the predetermined shift speed. ing,
An automatic transmission characterized by that. In claim 6 ,
When the select lever selects reverse travel, the two-way lock state is established and a reverse gear is configured.
An automatic transmission characterized by that. In any one of Claims 5 thru | or 7 ,
At power-off, the neutral state is assumed.
An automatic transmission characterized by that. In any one of Claims 5 thru | or 7 ,
When the power is turned off, the bidirectional lock state is set.
An automatic transmission characterized by that. In any one of Claims 1 thru | or 9 ,
The pocket portion, the strut and the spring member are each provided in the first coupling plate,
An automatic transmission characterized by that.

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