JP2011149499A - Hydraulic control valve - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To secure, in a hydraulic control valve configured to selectively supply pressure-adjusted hydraulic oil to a destination according to a shift range, sufficient fail toughness with a simple structure reduced in the number of part items by sharing of a device. <P>SOLUTION: The hydraulic control valve 1 includes a spool 20, a cylindrical sleeve 30 slidably receiving the spool 20, mechanical mechanisms 51, 55 for changing the rotating angle of the sleeve 30 according to the shift range, and a valve body 40 rotatably supporting the sleeve 30. An output port 34 provided in the sleeve 30 selectively communicates with any one of output oil passages 44a-44c provided in the valve body 40 according to the rotating angle of the sleeve 30, whereby the hydraulic oil adjusted in pressure by the spool 20 is delivered to the any one of the output oil passages 44a-44c and supplied to any one of hydraulic operating portions 72a-72c corresponding to the shift range, which is connected ahead. <P>COPYRIGHT: (C)2011,JPO&INPIT

Description

  The present invention relates to a hydraulic control valve installed in a hydraulic control circuit of a transmission, and more specifically, adjusts hydraulic oil from a hydraulic source such as an oil pump and controls a hydraulic operating unit for shifting such as a plurality of clutches. The present invention relates to a hydraulic control valve configured to be selectively supplied.

  The automatic transmission includes a hydraulic actuator mechanism for shifting such as a hydraulically operated clutch or a brake for operating an engagement element for setting a gear position. The hydraulic pressure supplied to the hydraulic actuator mechanism for shifting is controlled to set a desired shift speed. In order to control the supply hydraulic pressure, a hydraulic control mechanism is provided. In general, a hydraulic control mechanism switches a hydraulic pressure adjustment valve (linear solenoid valve) for adjusting hydraulic pressure of hydraulic oil from a hydraulic source such as an oil pump to a predetermined line pressure, and switching of hydraulic pressure supply to a plurality of hydraulic actuator mechanisms. And a switching valve (shift valve) for performing.

  As described above, in the hydraulic control mechanism of the automatic transmission, the shift valve switches the hydraulic pressure supply destination in accordance with the shift range. However, the shift valve has a problem of occurrence of failure such as spool sticking. Therefore, from the standpoint of ensuring fail-safety, it is desirable to switch the hydraulic pressure supply destination with a manual valve that can switch the hydraulic path reliably with a mechanical mechanism that is linked to the stroke of the select lever.

  When switching the hydraulic pressure supply destination according to the shift range using a manual valve, for example, the hydraulic pressure adjusted by one linear solenoid valve is used as the RVS clutch pressure in the R range, and the L / C control is used in the D range. It is used as a pressure, and in the L range, it is used as a low hold clutch pressure.

  However, since the manual valve only has an axial stroke operation, in order to switch the destination of the hydraulic oil supplied from one linear solenoid valve for each shift range, the number of shift ranges on the manual valve is the same as the number of shift ranges. It is necessary to provide an oil passage switching unit. For this purpose, a large number of oil passage switching portions must be arranged side by side along the longitudinal direction of the manual valve. Therefore, there is a problem that the length dimension of the manual valve is increased. In addition, when it is impossible to install a manual valve, the number of devices increases as a result, resulting in a problem that the hydraulic control mechanism is complicated.

  Therefore, instead of a manual valve that strokes in the axial direction, it is conceivable to adopt a structure in which the hydraulic pressure supply path can be switched by operation in the rotational direction. As a conventional example related to this, there is a hydraulic control mechanism shown in Patent Document 1. The hydraulic control mechanism disclosed in Patent Document 1 includes a rotary valve having a configuration in which an outlet port selectively communicates with a plurality of shift hydraulic actuators according to the rotation of a spool.

Japanese Patent No. 2937276

  However, the rotary valve shown in Patent Document 1 has a structure in which the rotation of the spool is controlled by a step motor. Therefore, when failure of the step motor and its drive circuit (actuator failure) is taken into account, reliable fail toughness can be obtained. There is no problem.

  Moreover, in the hydraulic control mechanism provided with the rotary valve shown in Patent Document 1, a hydraulic pressure adjustment valve and a rotary valve for switching the hydraulic pressure supply path are separately provided. In addition, a plurality of oil passages communicating the rotary valve and the hydraulic pressure source are provided, and the hydraulic pressure adjusting valves are respectively disposed in the respective oil passages. As a result, there are many components necessary for the hydraulic control mechanism such as the valves and the oil passages communicating with the valves. Therefore, there is a problem that it is not very suitable for simplifying and reducing the weight of the hydraulic control mechanism.

  The present invention has been made in view of the above points, and in a hydraulic control valve having a structure in which regulated hydraulic oil is switched and supplied to a predetermined destination, a simple structure in which the number of parts is reduced by sharing devices. An object is to ensure sufficient fail toughness while reducing the size.

  In order to solve the above problems, a hydraulic control valve according to the present invention includes an actuator section (10) having an actuator (11), a spool (20) driven by an output of the actuator (11), and a spool (20). A cylindrical sleeve (30) slidably accommodated in the forward / backward direction and a valve body (40) that rotatably supports the sleeve (30) are provided. The valve body (40) includes a hydraulic power source (71 ) Connected to the input oil passage (43), the plurality of hydraulic operation portions (72a to 72c), the plurality of output oil passages (44a to 44c), and the hydraulic release portion (73). A drain oil passage (45, 46) is formed, and the sleeve (30) has an input port (33) communicating with the input oil passage (43) and a plurality of output oil passages (44a to 44c). Selective with one of An output port (34) capable of communication and a discharge port (35) communicating with the discharge oil passage (45) are formed, and a sleeve (from the input oil passage (43) through the input port (33) ( 30) The hydraulic oil introduced into the spool (20) is pressure-balanced, and the output port (34) is one of the plurality of output oil passages (44a to 44c) according to the rotation angle of the sleeve (30). The hydraulic oil pressure-regulated by the spool (20) is led out to the output oil passage (44a or 44b or 44c) communicating with the output port (34) by selectively communicating with the hood.

  In the hydraulic control valve described above, the hydraulic actuator (72) is a hydraulic actuator mechanism (72) for setting the gear position provided in the transmission, and includes a rotation drive mechanism (50) for rotating the sleeve (30). The rotation drive mechanism (50) is configured to change the rotation angle of the sleeve (30) via the mechanical mechanism (51, 55) in accordance with each shift range selected by the shift range selection means (60). The plurality of output oil passages (44a to 44c) may be connected to hydraulic actuator mechanisms (72a to 72c) corresponding to the respective shift ranges.

  According to the hydraulic control valve of the present invention, the output port selectively communicates with any one of the plurality of output oil passages according to the rotation angle of the sleeve, so that the hydraulic oil regulated by the spool is connected to the output port. It is led out to a communicating output oil passage. Accordingly, it is possible to realize a hydraulic control valve that has both a function as a pressure regulating valve by a spool driven by an actuator and a function as a switching valve that switches a hydraulic pressure supply path in accordance with the rotation angle of the sleeve. As a result, the hydraulic control valve that can switch and supply the regulated hydraulic oil to a predetermined destination can be miniaturized with a simple structure that reduces the number of parts by sharing devices.

  Further, in this hydraulic control valve, the output port is configured to selectively communicate with any one of the plurality of output oil passages according to the rotation angle of the sleeve, so that a plurality of manual valves with only an axial stroke operation are provided. Compared to the case where the hydraulic pressure supply path is switched, the dimensions (particularly, the length dimension) of the hydraulic control valve can be reduced. In addition, the number of devices required for hydraulic switching can be reduced. Furthermore, since the sleeve for switching the hydraulic pressure supply path is provided integrally with the spool, the number of parts can be reduced, the configuration can be simplified, and the size can be reduced.

  In the hydraulic control valve according to the present invention, the rotation drive mechanism is configured to change the rotation angle of the sleeve via a mechanical mechanism in accordance with each shift range selected by the shift range selection means. As a result, the switching of the hydraulic oil supply destination can be reliably linked to the shift range switching. Therefore, it is possible to ensure a sufficient fail toughness while having a compact structure with a reduced number of parts.

  In the hydraulic control valve described above, the rotation drive mechanism (50) includes a control shaft (51) that rotates in conjunction with the selection of the shift range by the select lever (60), and the rotation of the control shaft (51). It is good to provide the link mechanism (55) which transmits to a sleeve (30). The sleeve (30) rotates integrally with the actuator section (10), and the rotation drive mechanism (50) rotates the sleeve (30) via the actuator section (10). Good. According to these, a mechanical mechanism for changing the rotation angle of the sleeve according to each shift range can be realized with a simple configuration. In addition, since the sleeve is rotated using a control shaft provided in the transmission, the number of parts of the rotational drive mechanism can be reduced, and space can be saved.

  In the hydraulic control valve described above, an input is made to at least one of the outer peripheral surface (30a) of the sleeve (30) and the inner peripheral surface (42a) of the valve body (40) regardless of the rotation angle of the sleeve (30). An input groove (33a) for communicating the oil passage (43) with the input port (33) or a passage for allowing the discharge oil passage (45) to communicate with the discharge port (35) regardless of the rotation angle of the sleeve (30). A discharge groove (35a) may be formed. According to this, regardless of the rotation angle of the sleeve (30), the input oil passage (43) communicates with the input port (33) or the discharge oil passage (45) and the discharge port (35). Communication will be secured.

In the hydraulic control valve, the sleeve (30) has an output oil passage (44a and 44b, or 44b and 44b and 44b) that is not in communication with the output port (34) among the plurality of output oil passages (44a to 44c). 44c or 44c and 44a) may be formed with a groove (34a) for communicating with the drain oil passage (46). According to this, with a simple configuration, the output oil passage that is not in communication with the output port can be communicated with the discharge oil passage, and the hydraulic pressure of the hydraulic operation unit that is not in communication with the output port can be released.
In addition, the code | symbol in said parenthesis shows the code | symbol of the corresponding component in embodiment mentioned later as an example of this invention.

  According to the hydraulic control valve of the present invention, sufficient fail toughness can be ensured while achieving downsizing with a simple structure in which the number of parts is reduced by sharing devices.

It is the schematic which shows the structural example of the hydraulic control valve concerning 1st Embodiment of this invention. (A) thru | or (c) are respectively AA, BB, CC schematic sectional drawing of FIG. It is a perspective view which shows the sleeve and actuator part of a hydraulic control valve. It is a figure for demonstrating operation | movement of a hydraulic control valve, (a) thru | or (c) is a figure which shows the communication state of the oil path in R range, D range, and L range, respectively. It is a figure which shows the structural example of the hydraulic control valve concerning 2nd Embodiment of this invention, (a) is a schematic side view (partial sectional drawing) of a hydraulic control valve, (b) shows a sleeve and an actuator part. It is a perspective view. (A), (b) is DD, EE schematic sectional drawing of FIG. 5, respectively.

Hereinafter, embodiments of the present invention will be described in detail with reference to the accompanying drawings.
[First Embodiment]
FIGS. 1 to 3 are diagrams showing a configuration example of a hydraulic control valve according to the first embodiment of the present invention. FIG. 1 is a schematic view of a hydraulic control valve 1, and FIGS. 2A to 2C are schematic cross-sectional views taken along lines AA, BB, and CC in FIG. 1, respectively. FIG. 3 is a perspective view showing the sleeve 30 and the actuator unit 10 provided in the hydraulic control valve 1. As shown in these drawings, the hydraulic control valve 1 is a valve device that supplies hydraulic pressure for controlling a hydraulic operation part (hydraulic actuator mechanism) 72 for shift control in an automatic transmission (the whole configuration is not shown). In this case, it has a function as a pressure regulating valve by the spool 20 driven by the linear solenoid 11 and a function as a rotary type switching valve for switching the output oil passage 44 in accordance with the rotation angle of the sleeve 30. It is.

  The hydraulic control valve 1 includes an actuator unit 10 including a linear solenoid (electromagnetic actuator) 11, a spool 20 that is driven forward by the output of the linear solenoid 11, a return spring 21 that biases the spool 20 in the backward direction, and a spool The cylindrical sleeve 30 which accommodated 20 in the forward / backward direction so that sliding was possible, and the valve body 40 which supports the sleeve 30 rotatably are provided. The sleeve 30 is accommodated in an accommodation hole 42 having a cylindrical inner peripheral surface 42 a provided in the valve body 40, and both ends of the sleeve 30 are rotatably supported by bearings 41, 41 in the accommodation hole 42. The sleeve 30 is rotated with respect to the spool 20 and the valve body 40 within the accommodation hole 42 by a rotation drive mechanism 50 described later. Note that the end portion of the sleeve 30 opposite to the actuator portion 10 is closed with a cap 22. One end of the return spring 21 installed in the sleeve 30 is fixed to the cap 22 and biases the spool 20 toward the actuator unit 10.

  An input oil passage 43, output oil passages 44 (44 a to 44 c), and a discharge oil passage 45 are opened on the inner peripheral surface 42 a of the accommodation hole 42 provided in the valve body 40. The input oil passage 43, the output oil passage 44, and the discharge oil passage 45 are arranged at predetermined intervals along the axial direction of the accommodation hole 42. As shown in FIG. 1, the input oil passage 43 is connected to an oil pump (hydraulic power source) 71, and the discharged oil passage 45 is opened to an oil tank (hydraulic release portion) 73. Moreover, as shown to Fig.2 (a), several output oil path 44a-44c is connected with each of several hydraulic operation part 72a-72c.

  As shown in FIG. 2A, first to third output oil passages 44 a to 44 c are provided as the output oil passage 44. The first to third output oil passages 44a to 44c are provided at the same position in the axial direction on the inner peripheral surface 42a of the accommodation hole 42, and are arranged radially at predetermined intervals along the circumferential direction. The first output oil passage 44a is connected to the RVS clutch 72a, the second output oil passage 44b is connected to the L / C control valve 72b, and the third output oil passage 44c is connected to the low hold clutch 72c. It is connected. As described above, the first to third output oil passages 44a to 44c are connected to the hydraulic operation units 72a to 72c for setting the respective gear positions of the transmission. Further, a discharge oil passage 46 is opened at the same position as the first to third output oil passages 44a to 44c in the axial direction. The drain oil passage 46 opens at a phase different from that of the first to third oil passages 44 a to 44 c and is opened to the oil tank 73.

  As shown in FIG. 1, the sleeve 30 is formed with an input port 33, an output port 34, and a discharge port 35. The input port 33, the output port 34, and the discharge port 35 are provided at positions corresponding to the input oil passage 43, the output oil passage 44, and the discharge oil passage 45, respectively, along the axial direction of the sleeve 30. The input port 33, the output port 34, and the discharge port 35 are all through holes that penetrate from the inner peripheral side to the outer peripheral side of the sleeve 30.

  As shown in FIG. 3, an annular input groove 33a extending in the circumferential direction is formed at a position including the input port 33 on the outer peripheral surface 30a of the sleeve 30. An annular first discharge groove 35a extending in the direction is formed. The input groove 33a and the first discharge groove 35a are formed over the entire circumference of the sleeve 30 including the input port 33 or the discharge port 35, respectively. A second discharge groove 34 a extending in the circumferential direction is formed at the position of the output port 34 in the axial direction of the outer peripheral surface 30 a of the sleeve 30. The second discharge groove 34a is formed in a portion excluding the output port 34, and the output port 34 and the second discharge groove 34a are partitioned by a land portion 34b.

  The input port 33 is always in communication with the input oil passage 43 through the input groove 33 a regardless of the rotation angle of the sleeve 30. Further, the discharge port 35 always communicates with the discharge oil passage 45 via the first discharge groove 35 a regardless of the rotation angle of the sleeve 30. On the other hand, since the output port 34 is partitioned from the second discharge groove 34a by the land portion 34b, the output port 34 is selectively communicated with any one of the plurality of output oil passages 44a to 44c according to the rotation angle of the sleeve 30. It has become.

  As shown in FIG. 1, the rotary drive mechanism 50 includes a control shaft 51 that rotates in conjunction with the selection of a shift range by a select lever (shift range selection means) 60, and the rotation of the control shaft 51 to the actuator unit 10. And a link mechanism 55 for transmission. Thus, the rotation angle of the sleeve 30 is changed according to the shift range selected by the select lever 60. The select lever 60 is a lever that is disposed in the driver's seat of the automobile and is manually operated by a driver. In response to the operation of the select lever 60, each shift range such as P (parking), R (reverse), N (neutral), D (D range), and L (low) is selected. And the rotation angle position of the control shaft 51 changes according to each shift range.

  The link mechanism 55 includes a rod-like lever 56 that linearly moves back and forth according to the rotation of the control shaft 51, and a rotating piece 57 that is rotatably connected to the lever 56 by a link portion 58. The rotating piece 57 is fixed to the actuator unit 10. The sleeve 30 rotates integrally with the actuator unit 10, and the rotation drive mechanism 50 rotates the sleeve 30 via the actuator unit 10. With such a rotational drive mechanism 50, the rotational angle position of the sleeve 30 changes according to the selection of the shift range by the select lever 60.

  The operation of the hydraulic control valve 1 having the above configuration will be described in detail. 4A and 4B are diagrams for explaining the operation of the hydraulic control valve 1. FIGS. 4A to 4D are the output port 34 and the output oil passages 44a to 44c in the R range, the D range, the L range, and the N range, respectively. It is a figure which shows a communication state with. In the hydraulic control valve 1, first, hydraulic oil introduced into the sleeve 30 from the input oil passage 43 shown in FIG. 1 through the input port 33 is regulated by the balance of the spool 20 by the linear solenoid 11 and the return spring 21. The The output port 34 of the sleeve 30 selectively communicates with any of the first to third output oil passages 44 a to 44 c provided in the valve body 40 according to the rotation angle of the sleeve 30 by the rotation drive mechanism 50. As a result, the hydraulic oil regulated by the spool 20 is led to any one of the first to third output oil passages 44 a to 44 c communicating with the output port 34.

  In this case, the output port 34 communicates with the first output oil passage 44a in the R range, the output port 34 communicates with the second output oil passage 44b in the D range, and the output port 34 communicates with the third output in the L range. It communicates with the oil passage 44c. In the N range and the P range, the output port 34 is blocked by the inner peripheral surface 42 a of the accommodation hole 42.

  That is, when the R range is selected by the select lever 60, the output port 34 communicates with the first output oil passage 44a as shown in FIG. Thereby, the hydraulic oil pressure-regulated by the spool 20 is led out to the first output oil passage 44a and supplied to the RVS clutch 72a (see FIG. 2A) ahead. Therefore, the RVS clutch 72a is engaged with the hydraulic pressure of the hydraulic oil. At this time, the second output oil passage 44b and the third output oil passage 44c not communicating with the output port 34 communicate with the discharge oil passage 46 via the second discharge groove 34a.

  When the D range is selected by the select lever 60, the output port 34 of the sleeve 30 communicates with the second output oil passage 44b of the valve body 40 as shown in FIG. As a result, the hydraulic oil regulated by the spool 20 is led out to the second output oil passage 44b and supplied to the L / C control valve 72b (see FIG. 2A) ahead. Therefore, the L / C control valve 72b is controlled by the hydraulic oil pressure. At this time, the first output oil passage 44a and the third output oil passage 44c not communicating with the output port 34 communicate with the discharge oil passage 46 through the second discharge groove 34a.

  When the L range is selected by the select lever 60, the output port 34 of the sleeve 30 communicates with the third output oil passage 44c of the valve body 40 as shown in FIG. As a result, the hydraulic oil regulated by the spool 20 is led out to the third output oil passage 44c and supplied to the low hold clutch 72c (see FIG. 2A). Therefore, the low hold clutch 72c is engaged by the hydraulic pressure of the hydraulic oil. At this time, the first output oil passage 44a and the second output oil passage 44b that are not in communication with the output port 34 communicate with the discharge oil passage 46 through the second discharge groove 34a.

  Accordingly, the hydraulic oil regulated by the spool 20 of the hydraulic control valve 1 is supplied to the RVS clutch 72a in the R range, supplied to the L / C control valve 72b in the D range, and supplied to the low hold clutch 72c in the L range. Is done. At this time, of the output oil passages 44a to 44c, two portions that do not communicate with the output port 34 communicate with the discharge oil passage 46 through the second discharge groove 34a.

  As described above, in the hydraulic control valve 1 of the present embodiment, the actuator unit 10 having the linear solenoid 11, the spool 20 driven by the output of the linear solenoid 11, and the spool 20 are slidably accommodated in the forward / backward direction. A cylindrical sleeve 30 and a valve body 40 that rotatably supports the sleeve 30 are provided. The valve body 40 is opened to an input oil passage 43 connected to the oil pump 71, a plurality of output oil passages 44a to 44c connected to each of the plurality of hydraulic operating portions 72a to 72c, and an oil tank 73. The discharge oil passages 45 and 46 are formed, and the sleeve 30 can selectively communicate with the input port 33 communicating with the input oil passage 43 and any of the plurality of output oil passages 44a to 44c. An output port 34 and a discharge port 35 communicating with the discharge oil passage 45 are formed. In such a configuration, the hydraulic oil introduced into the sleeve 30 from the input oil passage 43 through the input port 33 is regulated by the balance of the spool 20. Then, according to the rotation angle of the sleeve 30, the output port 34 selectively communicates with any of the plurality of output oil passages 44 a to 44 c, so that the hydraulic oil regulated by the spool 20 communicates with the output port 34. It is led out to any one of the output oil passages 44a to 44c.

  Further, in the present embodiment, a rotation drive mechanism 50 that rotates the sleeve 30 is provided, and the rotation drive mechanism 50 is connected to the sleeve via the control shaft 51 and the link mechanism 55 in accordance with each shift range selected by the select lever 60. The rotation angle of 30 is changed. The first to third output oil passages 44a to 44c are connected to an RVS clutch 72a, an L / C control valve 72b, and a low hold clutch 72c, which are hydraulic actuator mechanisms corresponding to the R range, the D range, and the L range, respectively. ing.

  According to the hydraulic control valve 1 of the present embodiment, the output port 34 selectively communicates with any of the first to third output oil passages 44 a to 44 c according to the rotation angle of the sleeve 30, so that the spool 20 The adjusted hydraulic fluid is led out to any one of the output oil passages 44 a to 44 c communicating with the output port 34. Therefore, it has a function as a pressure regulating valve by the spool 20 driven by the linear solenoid 11 and a function as a switching valve for switching the hydraulic pressure supply path according to the rotation angle of the sleeve 30. As a result, the hydraulic control valve 1 capable of switching and supplying the regulated hydraulic oil to a predetermined destination can be miniaturized with a simple structure in which the number of parts is reduced by sharing devices.

  Further, in the hydraulic control valve 1, the output port 34 is configured to selectively communicate with any one of the first to third output oil passages 44 a to 44 c according to the rotation angle of the sleeve 30. Therefore, the size (particularly the length) of the hydraulic control valve 1 can be reduced as compared with the case where a plurality of hydraulic pressure supply paths are switched. In addition, the number of devices required for hydraulic switching can be reduced. Furthermore, since the sleeve 30 for switching the hydraulic pressure supply path is installed integrally with the spool 20, the number of parts can be reduced, the configuration can be simplified, and the size can be reduced.

  Further, in the hydraulic control valve 1 of the present embodiment, the rotation drive mechanism 50 transmits the rotation of the control shaft 51 to the sleeve 30 and the control shaft 51 that rotates in conjunction with the setting of the shift stage by the select lever 60. The link mechanism 55 is comprised. As described above, the rotation drive mechanism 50 is configured to change the rotation angle of the sleeve 30 via the mechanical mechanism in accordance with each shift range set by the select lever 60. Therefore, switching of the hydraulic oil supply destination can be reliably linked to switching of the shift range. Therefore, it is possible to ensure sufficient fail toughness while having a compact structure with a reduced number of parts.

  In addition, since the rotary drive mechanism 50 is configured to rotate the sleeve 30 using the control shaft 51 provided in the transmission, the number of parts of the rotary drive mechanism 50 can be reduced and space saving can be achieved. Can do. Further, the sleeve 30 rotates integrally with the actuator unit 10, and the rotation drive mechanism 50 rotates the sleeve 30 via the actuator unit 10. Thereby, a mechanical mechanism for changing the rotation angle of the sleeve 30 according to each shift range is realized with a simple configuration.

  Further, in the hydraulic control valve 1 of the present embodiment, the output oil passage 44 not communicating with the output port 34 is communicated with the discharge oil passage 46 by the second discharge groove 34 a formed in the sleeve 30. Accordingly, since the output oil passage 44 that is not in communication with the output port 34 can be communicated with the discharge oil passage 46 with a simple configuration, the hydraulic pressure that is connected to the output oil passage 44 that is not in communication with the output port 34. The hydraulic pressure of the operating part 72 can be released.

[Second Embodiment]
Next, a second embodiment of the present invention will be described. In the description of the second embodiment and the corresponding drawings, the same or corresponding components as those in the first embodiment are denoted by the same reference numerals, and detailed description thereof will be omitted below. In addition, matters other than those described below are the same as those in the first embodiment. This is the same in other embodiments.

  FIG. 5 is a diagram showing a configuration example of a hydraulic control valve 1-2 according to the second embodiment of the present invention, and (a) is a schematic side view (partially sectional view) of the hydraulic control valve 1-2. FIG. 7B is a perspective view showing the sleeve 30 and the actuator unit 10. FIGS. 6A and 6B are schematic sectional views taken along the lines DD and EE of FIG. 5, respectively. In FIG. 5A, a part of the rotation drive mechanism 50 is not shown. As shown in these drawings, in the hydraulic control valve 1-2 of the present embodiment, the input groove 33a and the first discharge groove 35a provided in the outer peripheral surface 30a of the sleeve 30 in the hydraulic control valve 1 of the first embodiment are provided. Instead, an input groove 43a and a first discharge groove 45a provided on the inner peripheral surface (inner peripheral surface of the receiving hole 42) 42a of the valve body 40 are provided. The input groove 43 a is an annular groove provided at the position of the input oil passage 43 in the axial direction of the accommodation hole 42. Further, the first discharge groove 45 a is an annular groove provided at the position of the discharge oil passage 45 in the axial direction of the accommodation hole 42.

  The input port 33 and the discharge port 35 of the sleeve 30 must always communicate with the input oil passage 43 and the discharge oil passage 45 of the valve body 40 regardless of the rotation angle of the sleeve 30. As a configuration for this, in the first embodiment, the input groove 33a and the first discharge groove 35a formed on the outer peripheral surface 30a of the sleeve 30 are provided. However, the input groove 33a and the first discharge groove 35a are not necessarily provided on the sleeve 30 side, and can be provided on the valve body 40 side as in this embodiment. As described above, the input groove 43a and the first discharge groove 45a provided on the inner peripheral surface 42a of the valve body 40 can ensure the same functions as the input groove 33a and the first discharge groove 35a of the first embodiment. It becomes possible.

  Although the embodiments of the present invention have been described above, the present invention is not limited to the above-described embodiments, and various modifications can be made within the scope of the technical idea described in the claims and the specification and drawings. Is possible. For example, the RVS clutch 72a, the L / C control valve 72b, and the low hold clutch 72c shown in the above embodiment are examples of a hydraulic operation unit (hydraulic actuator mechanism) provided in the hydraulic control valve according to the present invention. A clutch, a brake, a valve, or the like of a type other than that shown in the above embodiment may be used. Further, the number and arrangement of output oil passages shown in the above embodiment are examples, and the specific number and arrangement of output oil passages are not limited to those shown in the above embodiment.

1, 1-2 Hydraulic control valve 10 Actuator section 11 Linear solenoid (actuator)
20 Spool 30 Sleeve 33 Input port 33a Input groove 34 Output port 34a Second discharge groove (other discharge grooves)
34b Land portion 35 Discharge port 35a First discharge groove (discharge groove)
40 Valve body 42 Housing hole 43 Input oil passage 43a Input groove 44 Output oil passage 44a First output oil passage 44b Second output oil passage 44c Third output oil passage 45 Discharge oil passage 45a Discharge groove 46 Discharge oil passage 50 Rotation drive mechanism 51 Control shaft 55 Link mechanism 56 Lever 57 Rotating piece 58 Link portion 60 Select lever (shift range selection means)
72 Hydraulic actuator (hydraulic actuator mechanism)
72a RVS clutch 72b L / C control valve 72c Low hold clutch 73 Oil tank (hydraulic release part)

Claims (6)

An actuator unit having an actuator; a spool driven by the output of the actuator; a cylindrical sleeve that slidably accommodates the spool in a forward and backward direction; and a valve body that rotatably supports the sleeve. ,
The valve body is formed with an input oil passage connected to a hydraulic pressure source, a plurality of output oil passages connected to each of a plurality of hydraulic operation portions, and a discharge oil passage opened to the hydraulic release portion. ,
The sleeve includes an input port that communicates with the input oil passage, an output port that can selectively communicate with any of the plurality of output oil passages, and a discharge port that communicates with the discharge oil passage. Formed,
The hydraulic oil introduced into the sleeve from the input oil passage through the input port is regulated by the balance of the spool,
Depending on the rotation angle of the sleeve, the output port selectively communicates with any of the plurality of output oil passages, so that the hydraulic oil regulated by the spool enters the output oil passage communicated with the output port. Hydraulic control valve characterized by being derived. The hydraulic operation unit is a hydraulic actuator mechanism for setting a gear stage provided in the transmission,
A rotation drive mechanism for rotating the sleeve;
The rotation drive mechanism is configured to change the rotation angle of the sleeve via a mechanical mechanism in accordance with each shift range selected by the shift range selection unit.
2. The hydraulic control valve according to claim 1, wherein each of the plurality of output oil passages is connected to a hydraulic actuator mechanism corresponding to each of the shift ranges. 3. The rotation drive mechanism includes a control shaft that rotates in conjunction with selection of a shift range by a select lever, and a link mechanism that transmits the rotation of the control shaft to the sleeve. Hydraulic control valve as described in. The sleeve is configured to rotate integrally with the actuator unit,
The hydraulic control valve according to any one of claims 1 to 3, wherein the rotation driving mechanism rotates the sleeve via the actuator unit. At least one of the outer peripheral surface of the sleeve and the inner peripheral surface of the valve body has an input groove for communicating the input oil passage with the input port regardless of the rotation angle of the sleeve, or the rotation of the sleeve The hydraulic control valve according to any one of claims 1 to 4, wherein a discharge groove is formed for communicating the discharge oil passage with the discharge port regardless of an angle. In the outer peripheral surface of the sleeve, another discharge groove is formed to connect an output oil passage that is not in communication with the output port among the plurality of output oil passages to the discharge oil passage. The hydraulic control valve according to any one of claims 1 to 5.

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