JP6501641B2 - Flow control valve - Google Patents

Description

  The present invention relates to, for example, a flow control valve used for flow control of cooling water for vehicles.

  For example, as a conventional flow control valve applied to flow control of cooling water for vehicles, what was indicated, for example in the following patent documents 1 is known.

  This flow control valve is a so-called rotary type valve that performs flow control in accordance with the rotational position (phase) of the rotor, which is a substantially cylindrical valve body, and is opened by polymerization between the opening of the housing and the opening of the rotor. The valve is closed by pressing the cylindrical seal member against the outer peripheral wall which is the non-opening portion of the rotor with the biasing force of the elastic member resiliently mounted on the opening portion of the housing.

German Patent Application Publication No. 2011083803

  However, in the conventional flow control valve, as described above, the sealability is secured by pressing the seal member against the outer peripheral wall of the rotor with the biasing force of the elastic member. For this reason, if the biasing force of the elastic member is increased to improve the sealing performance, the sliding resistance of the rotor is also increased along with the biasing force, which may deteriorate the operability of the rotor. was there.

  The present invention has been made in view of such technical problems, and it is an object of the present invention to provide a flow control valve capable of improving sealing performance while securing good operability of a rotor.

  According to the present invention, an inlet provided in a hollow valve body accommodating portion and used for introducing a fluid, and an axial direction outlet communicating with the valve body accommodating portion in an axial direction to discharge fluid in the valve body accommodating portion A valve body rotatably supported in the housing, the valve body having an axial opening whose polymerization state with the axial discharge port changes according to the rotational position, the housing, and the valve body And an axial seal member for sealing between the housing and the valve body in the axial direction by being in sliding contact with the outer peripheral surface of the valve body. It is characterized in that it is axially moved in the direction in which it is in pressure contact with the axial seal member as the axial opening rotates in a direction in which the amount of polymerization of the axial opening decreases with respect to the direction discharge port.

  Here, as a preferable mode of the present invention, an actuator for driving and controlling the valve body, and a driving mechanism for driving the valve body by transmitting a driving force of the actuator to the valve body are further provided. It is preferable that a thrust force generated in the drive mechanism acts in a direction of pressing the axial seal member against the valve body as the actuator is driven.

  With this configuration, the axial seal member is pressed against the valve body at the time of rotation in the valve closing direction by the thrust force generated in the drive mechanism used to transmit the drive force of the actuator, thereby obtaining the axial seal member, Relatively high sealing performance can be ensured as compared with the unnecessary valve opening of the seal.

  Moreover, in order to use the thrust force generated by the drive mechanism necessary for driving the valve body, there is no need to add another configuration separately, and the above-mentioned good operability and shaft of the valve body with a relatively simple structure The coexistence with the favorable sealability of a direction seal member is realizable.

  According to the present invention, the valve body can be brought into pressure contact with the axial seal member at the time of valve closing where sealing is required, and a relatively higher sealing performance can be secured as compared to the time of unnecessary valve opening of the seal. It is possible to improve the sealing performance of the axial direction sealing member while securing the rigidity.

FIG. 2 is a cooling water circuit diagram for describing application of a flow control valve according to the present invention to a circulation system of cooling water for a vehicle. It is an exploded perspective view of a flow control valve concerning the present invention. It is a front view of the flow control valve shown in FIG. It is the sectional view on the AA line of FIG. It is the BB sectional drawing of FIG. It is a side view of the flow control valve shown in FIG. It is the CC sectional view taken on the line of FIG. It is a longitudinal cross-sectional view of the fail-safe valve shown in FIG. 5, Comprising: (a) is a valve closing state, (b) is a figure which shows an valve opening state. It is a perspective view of the valve body shown in FIG. 2, Comprising: (a)-(d) is a figure which shows the state seen from another viewpoint, respectively. It is a figure where it uses for operation explanation of a flow control valve concerning the present invention, and (a) is a state where all the discharge ports become non-communicating, (b) a state where only the first discharge port is in communication, (c) The state which the 1st, 2nd discharge port connected, and (d) are the expanded views of the valve body accommodating part which shows the state which all the discharge ports connected. It is a figure which is provided to the effect | action description of the flow control valve which concerns on this invention, Comprising: (a) is a fragmentary sectional view of the flow control valve at the time of valve closing, (b) is a principal part enlarged view of the figure (a). It is a figure which is provided to the effect | action description of the flow control valve which concerns on this invention, Comprising: (a) is a fragmentary sectional view of the flow control valve at the time of valve opening, (b) is a principal part enlarged view of the figure (a).

  Hereinafter, an embodiment of a flow control valve according to the present invention will be described based on the drawings. In the following embodiment, a flow control valve according to the present invention is applied to a circulating system of automobile cooling water (hereinafter simply referred to as "cooling water") similar to the conventional one will be described as an example.

  First, the circulation circuit of the coolant to which the flow control valve CV is applied will be described. As shown in FIG. 1, the flow control valve CV is on the side of the engine EG (specifically, a cylinder head not shown). The engine EG is disposed between the engine EG and the heating heat exchanger HT (EGR cooler EC), the oil cooler OC and the radiator RD. Then, the cooling water pressurized by the water pump WP and guided to the flow control valve CV through the introduction passage L0 is heated through the first to third pipes L1 to L3 and the heating heat exchanger HT, the oil cooler OC, and the radiator RD. Each flow is distributed to the side, and each flow rate is controlled. At this time, the cooling water led to the heating heat exchanger HT is led to the EGR cooler EC, and then returned to the engine EG side.

  Further, the flow rate control valve CV is provided with a bypass passage BL which bypasses the introduction passage L0 and directly guides the cooling water to the throttle chamber TC. With the bypass passage BL, the cooling water led from the engine EG side Can be constantly supplied to the throttle chamber TC via the fourth pipe L4. Then, the cooling water supplied to the throttle chamber TC is led to the EGR cooler EC as in the case of the heating heat exchanger HT, and is recirculated to the engine EG side through the EGR cooler EC. The symbol WT in FIG. 1 indicates a water temperature sensor.

  Subsequently, the specific configuration of the flow rate control valve CV will be described. As shown in FIGS. 2 to 7, the flow rate control valve CV is a first housing 11 that accommodates the valve body 3 and the electric motor 4 described later. And one end wall 11b of the first housing 11 separating the first housing 11 and the second housing 12 from each other through the housing 1 including the second housing 12 accommodating the speed reduction mechanism 5 described later, and the one end wall 11b, a rotary shaft 2 rotatably supported by a bearing B1 and a substantially cylindrical valve body 3 fixed to one end of the rotary shaft 2 and rotatably housed in the first housing 11 Between the motor output shaft 4 c of the electric motor 4 and the rotary shaft 2, the electric motor 4 disposed in parallel with the valve body 3 in the first housing 11 and providing drive control of the valve body 3. The electric motor 4 A speed reduction mechanism 5 for transmitting rotation speed is decelerated, and is mainly comprised.

  The first housing 11 is cast by an aluminum alloy material, and a substantially cylindrical valve body accommodating portion 13 for accommodating the valve body 3 biased toward one end side in the width direction is opened toward the one end side in the axial direction A substantially cylindrical motor accommodating portion 14 accommodating the electric motor 4 is opened toward the other end in the axial direction while being formed and biased to the other end in the width direction adjacent to the valve body accommodating portion 13. Not shown on the side of the engine (not shown) via a first flange portion 11a which is formed and extends in the outer peripheral area of the inlet 10 described later which is formed in the peripheral area of one end side of the valve body housing 13 It is fixed by the bolt of.

  The valve body accommodation portion 13 has an inlet port 10 communicating with the inside of the engine (not shown) and serving to introduce cooling water from the inside of the engine open in the circumferential region at the one end side. The cooling water is guided to the inner peripheral passage 17 and the outer peripheral passage 18 respectively formed on the inner peripheral side and the outer peripheral side of the valve body 3. Furthermore, by connecting the first and second pipes L1 and L2 (see FIG. 1) to the peripheral wall of the valve body accommodating portion 13, substantially cylindrical first and second discharge ports E1 to be used for discharging the cooling water. , And E2 are radially formed to be mutually offset in the axial direction, and are connected to the third pipe L3 (see FIG. 1) at the other end wall 11c of the valve body accommodation portion 13. A substantially fan-shaped third discharge port E3 for discharging the cooling water is formed to penetrate in the axial direction.

  Here, the first to third discharge ports E1 to E3 are connected to the first to third pipes L1 to L3 (see FIG. 1) via first to third discharge pipes P1 to P3 described later, respectively. It has become so. That is, in the outer peripheral portion of the valve body accommodation portion 13, first and second outlets O1 and O2 constituting first and second discharge pipes P1 and P2, which will be described later, respectively, and in the valve body accommodation portion 13 At the other end, a third outlet O3 constituting a third discharge pipe P3 described later is attached and fixed by a plurality of bolts BT1.

  The first and second outlets O1 and O2 have flanges O1a and O2a for fixing the first and second outlets E1 and E2 to the outer end side opening edge, and outer sides of the flanges O1a and O2a. The first and second discharge pipes P1 and P2, which are formed to project and guide the cooling water discharged from the first and second discharge ports E1 and E2 to the first and second pipes L1 and L2, are integrally formed. It is configured by.

  The third outlet O3 is formed on the other end side of the valve body housing 13 so as to protrude from the flange O3a for attachment and fixation to the outer end side opening edge of the third outlet E3, and to the outside of the flange O3a. The third discharge pipe P3 for guiding the cooling water that has flowed out of the third discharge port E3 and the communication port 26 described later to the third pipe L3 is integrally formed.

  Further, on the inner peripheral side of the first and second discharge ports E1 and E2, when the first and second discharge ports E1 and E2 are closed, the space between the respective discharge ports E1 and E2 and the valve body 3 is Sealing means are provided for sealing in a liquid tight manner. The sealing means is accommodated so as to be movable forward and backward on the inner end side of each discharge port E1, E2, and seals between the discharge port E1, E2 and the valve body 3 by sliding contact with the outer peripheral surface of the valve body 3. Openings of the respective discharge pipes P1, P2 in a form of being seated on the opening edges of the respective discharge pipes P1, P2 at the outer end sides of the substantially cylindrical first and second seal members S1, S2 and the respective discharge ports E1, E2. The first and second coil springs SP1 and SP2 are resiliently mounted between the edge and the inner end surfaces of the seal members S1 and S2 with a predetermined preload to bias the seal members S1 and S2 to the valve body 3 side. It consists mainly of SP2.

  The first and second seal members S1 and S2 are formed on the inner peripheral edge on one end side to be the valve body 3 side in a substantially conical tapered shape in sliding contact with the first and second seal sliding portions D1 and D2 described later The first and second valve body sliding contact portions S1a and S2a are provided, while the other ends have flat first and second ones in which one end sides of the first and second coil springs SP1 and SP2 are seated. Two seating surfaces S1b and S2b are formed. From this configuration, for each of the valve element sliding contact portions S1a and S2a, only the middle portion in the thickness width direction (radial direction) is in sliding contact with the seal sliding contact surfaces D1 and D2. It comes in sliding contact.

  Here, the sealing means is not limited to the physical sealing means by the sealing members S1 and S2. For example, a predetermined minute gap between the discharge ports E1 and E2 and the valve body 3 is provided. It is also possible to adopt a so-called clearance seal that seals by interposing the In the case of such a clearance seal structure, the structure of the flow control valve CV can be simplified, and there is an advantage that the productivity can be improved and the manufacturing cost can be reduced.

  Further, also on the inner peripheral side of the third discharge port E3, a sealing means is provided to seal between the third discharge port E3 and the valve body 3 in a liquid-tight manner when the third discharge port E3 is closed. It is done. This sealing means is constituted only by the third sealing member S3 which is a well-known O-ring, and includes biasing means by coil springs SP1 and SP2 such as sealing means by the first and second sealing members S1 and S2. Therefore, the valve body 3 is not always urged. Unnecessary pressure contact with the valve body 3 is thereby suppressed.

  Further, at the other end side outer peripheral portion of the valve body accommodating portion 13, the inner end side faces the outer peripheral side passage 18, and the fourth discharge pipe P4 is connected to the outer end side, so that the cooling water is throttle chamber TC. A fourth discharge port E4 is formed to penetrate to form a bypass passage BL (see FIG. 1). That is, with this configuration, the cooling water led to the outer circumferential side passage 18 is always discharged from the fourth discharge pipe P4 regardless of the rotational phase of the valve body 3 described later, and the fourth pipe L4 (see FIG. 1) It is possible to distribute to the throttle chamber TC via

  Furthermore, as shown in FIG. 2, FIG. 5 and FIG. 8, the valve body is housed in the side of the third discharge port E3 in an emergency, for example, when the valve body 3 becomes inoperable, such as when the electric system fails. A fail-safe valve 20 is provided to allow communication between the portion 13 (outer side passage 18) and the third discharge port E3 and secures the supply of cooling water to the radiator RD even in the immobile state of the valve body 3 By doing so, it is possible to prevent the engine EG from overheating.

  The fail safe valve 20 is inserted into a valve housing hole 11 d drilled from the other end wall 11 c of the valve body housing 13 so as to face the valve body housing 13, and the outer peripheral side passage 18 and the inner peripheral side A valve body 21 which is a substantially cylindrical flow path constituting member forming a communication port 26 as a flow path communicating with the third discharge pipe P3, and the inner end side of the valve body 21 are provided with a predetermined cooling water temperature. When the temperature is exceeded, the wax (not shown) filled inside is expanded and the rod 22a is fixed to the rod 22a of the thermo element 22 so that the rod 22a is advanced in the valve opening direction, the communication A valve member 23 serving to open and close the port 26 and a substantially disc-shaped rib supported on the outer end of the valve body 21 (a support piece 21c of the arm 21b described later) facing the valve member 23 And over Na member 24 is elastically installed with a predetermined preload between the retainer member 24 and the valve member 23, a coil spring 25 for biasing the valve member 23 and the valve closing direction, and is mainly comprised.

  The valve body 21 has a substantially stepped diameter shape, and is provided at a predetermined position in the circumferential direction on the outer end side of the small-diameter body main body 21a for accommodating and holding the thermoelement 22, and the retainer And a plurality of arm portions 21 b for supporting the member 24. A support piece 21c substantially in the shape of a claw is bent inward in the radial direction at the tip of each arm 21b, and the retainer 24 is supported by the support 21c. The structure is

  The valve member 23 is provided so as to cover the outer peripheral edge of the cored bar 23a for fixing the thermoelement 22 to the rod 22a, and the cored bar 23a, and has adhesiveness to the valve body 21 when the valve is closed. And a rubber coating 23b for improvement. Then, the communication port 26 is opened and closed by the cover 23 b of the valve member 23 being separated from and seated on the outer end opening edge of the body main body 21 a.

  In this manner, in the normal state (the cooling water temperature is lower than the predetermined temperature), the coating 23b of the valve member 23 is brought into pressure contact with the outer hole edge of the communication port 26 with the biasing force of the coil spring 25 to maintain the valve closing state. Be done. On the other hand, when the temperature becomes high (cooling water temperature exceeds a predetermined temperature), the wax in the thermoelement 22 expands and resists the biasing force of the coil spring 25 and the valve member 23 retracts to the outer end side together with the rod 22a. The cooling water which is opened by moving and is led to the outer peripheral side passage 18 is discharged from the third discharge pipe P3 through the communication port 26, and the radiator RD is transmitted through the third pipe L3 (see FIG. 1). Will be supplied to

  In addition to the rise of the cooling water temperature, the valve member 23 is also pushed open against the urging force of the coil spring 25 when the cooling water pressure exceeds a predetermined pressure, whereby the flow control valve CV is opened. As a result of the decrease in the internal pressure of the valve, it is possible to avoid the failure of the flow control valve CV.

  As shown in FIG. 2, the second housing 12 is opened so that one end opposite to the first housing 11 straddles the valve body accommodating portion 13 and the motor accommodating portion 14 so as to cover both the accommodating portions 13 and 14. The first housing 11 is fixed to one end side of the first housing 11 by a plurality of bolts BT2 via the second flange portion 12a which is formed in a concave shape and extends to the outer peripheral area of the one end side opening. A speed reduction mechanism housing portion 15 for housing the speed reduction mechanism 5 is formed between one end and the other. When the first and second housings 11 and 12 are joined, an annular seal member SL3 is interposed between the joint surfaces to hold the inside of the speed reduction mechanism accommodating portion 15 in a liquid-tight manner.

  The rotary shaft 2 is rotatably supported by a bearing B1 housed and disposed in a shaft insertion hole 11e formed through at one end wall 11b of the valve body housing 13 as shown in FIG. 2, FIG. 4 and FIG. The valve body 3 is fixed to one end in the axial direction, and a second bevel gear HG2 to be described later is fixed to the other end integrally and rotatably. An annular seal member SL4 is interposed between the outer peripheral surface of the rotation shaft 2 and the inner end opening edge of the shaft insertion hole 11e, and the shaft insertion hole 11e and the rotation are rotated by the seal member SL4. The inflow of cooling water from the valve body accommodation portion 13 side through the radial gap with the shaft 2 to the reduction mechanism accommodation portion 15 side is suppressed.

  As shown in FIG. 2, FIG. 4, FIG. 5, and FIG. 9, the valve body 3 is integrally formed into a substantially cylindrical shape by a predetermined synthetic resin material, and a central portion on one axial end side facing the one end wall 11b. In addition, a substantially cylindrical shaft fixing portion 3 a provided for mounting and fixing to the rotary shaft 2 is extended along the rotational axis direction of the valve body 3. A metal insert member (not shown) is integrally formed on the inner peripheral side of the shaft fixing portion 3a, and is press-fitted and fixed to the rotary shaft 2 through the insert member.

  Further, in the outer peripheral region of the shaft fixing portion 3a, an axial inlet 3b, which is a main flow inlet for causing the cooling water introduced through the inlet 10 to flow axially to the inner peripheral passage 17, is circumferentially The opening is formed over substantially the entire circumference of the. Furthermore, in the peripheral wall of the axial direction one end of the valve body 3, a radial inflow port 3c, which is an auxiliary inlet, which allows the cooling water introduced through the inlet 10 to radially flow into the inner circumferential passage 17. However, an opening is formed over a predetermined circumferential direction area of the valve body 3 (specifically, a circumferential direction area which can communicate with the inlet 10 regardless of the phase of the valve body 3).

  On the other hand, on the other end side in the axial direction of the valve body 3, a substantially spherical seal sliding contact portion is provided which is in sliding contact with the respective seal members S1 to S3 to provide a sealing action at the time of valve closing. That is, on the other end side in the axial direction of the valve body 3, the first seal sliding portion D1 in sliding contact with the first seal member S1 is in contact with the outer peripheral wall of the axial intermediate portion. A second seal sliding contact portion D2 in sliding contact with the second seal member S2 is provided, and a third seal sliding contact portion D3 in sliding contact with the third seal member S3 is provided on the outer surface of the other end wall 3d.

  The first seal sliding contact portion D1, as shown in FIG. 4, is provided along the circumferential direction on the outer peripheral wall of the axial intermediate portion of the valve body 3, and the predetermined circumferential direction of the first seal sliding contact portion D1 In the range, a long hole-shaped first opening M1 set to have an axial width that can be superposed with the first discharge port E1 almost without deficiency is provided along the circumferential direction of the valve body 3. Then, the communication between the first discharge port E1 and the inner peripheral side passage 17 through the first opening M1 enables supply of the cooling water to the oil cooler OC.

  Similarly, the second seal sliding contact portion D2 is provided along the circumferential direction on the outer peripheral wall of the other axial end portion of the valve body 3, and in the predetermined circumferential direction range of the second seal sliding contact portion D2. A slot-like second opening M2 is provided along the circumferential direction of the valve body 3 so as to have an axial width that can be polymerized almost without deficiency with the second discharge port E2. Then, the communication between the second discharge port E2 and the inner peripheral side passage 17 through the second opening M2 enables supply of the cooling water to the heater HT.

  In the third seal sliding contact portion D3, as shown in FIG. 5, a substantially arc-shaped third opening M3 set to a radial width that can overlap with the third discharge port E3 is a circumference of the valve body 3 It is provided along the direction. The third opening M3 is formed in an irregular shape in which the radial width varies in the circumferential direction, and the fan-shaped third outlet formed so as to have a substantially constant radial width in the circumferential direction. In the polymerization with E3, it is possible to change the polymerization area (the communication amount) with the third outlet E3 instead of the simple communication / non-communication.

  Further, as shown in FIG. 4 and FIG. 5, a support projection 3 e for providing rotational support on the other end side of the valve body 3 is provided on the outer central portion of the other end wall 3 d of the valve body 3. It is formed protruding along the rotational axis direction of the. The support projection 3 e is slidably engaged with a concave bearing hole 11 f formed in the inner side surface of the other end wall 11 c of the valve body accommodating portion 13, whereby rotation support of the other end of the valve body 3 is supported. Being served. Further, the support projection 3e is formed such that the tip end side is conical tapered and the tip end portion is substantially spherical, so that centering of the rotation axis of the other end side of the valve body 3 is possible. .

  The valve body 3 configured as described above is rotatably supported via the rotary shaft 2 and the support projection 3e, and is rotated within a predetermined angular range while slidingly contacting the seal members S1 to S3. By doing this, the opening and closing of each of the discharge ports E1 to E3 is performed. In the opening and closing of the discharge ports E1 to E3, the openings M1 to M3 are switched in communication with the discharge ports E1 to E3 in the order of first to fourth states described later shown in FIG. It is set.

  As shown in FIG. 2, the electric motor 4 is provided via the flange portion 4 b provided at the base end portion of the motor body 4 a in a state where the motor body 4 a is accommodated in the motor accommodating portion 14 of the first housing 11. The motor output shaft 4 c is attached and fixed to the opening edge of the motor housing 14 by a plurality of bolts (not shown), and the motor output shaft 4 c faces the inside of the speed reduction mechanism housing 15 of the second housing 12 through an opening at one end of the motor housing 14. The electric motor 4 is drive-controlled by an on-vehicle electronic controller (not shown), and the valve body 3 is controlled to rotate according to the vehicle operation state, whereby appropriate distribution of the cooling water to the radiator RD etc. is realized. To be realized.

  The reduction mechanism 5 is a drive mechanism configured by two worm gears, and is connected to a first worm gear G1 that cooperates with the motor output shaft 4c to reduce the rotation of the electric motor 4, and the first worm gear G1. The second worm gear G2 further decelerates the rotation of the electric motor 4 transmitted via the first worm gear G1 and transmits it to the rotating shaft 2, and the second worm gear G2 is connected to the first worm gear G1. It is arranged in a substantially orthogonal form.

  The first worm gear G1 is integrally provided on the outer periphery of the motor output shaft 4c, and a first screw gear WG1 integrally rotating with the motor output shaft 4c and the first screw gear WG1 substantially in parallel with the motor rotation shaft 4c. A first diagonal tooth provided integrally on one end side outer periphery of the rotary shaft 19 provided in a form orthogonal to the first gear, and decelerating and outputting the rotation of the first screw gear WG1 by meshing with the first screw gear WG1 And a gear HG1.

  The second worm gear G2 is integrally provided on the outer periphery of the other end of the rotary shaft 19, and is orthogonal to the second screw gear WG2 that rotates integrally with the first helical gear HG1 and the second screw gear WG2. A second diagonal tooth that is integrally rotatably fixed to the outer periphery of the other end of the rotary shaft 2 disposed in a shape, and decelerates and outputs the rotation of the second screw gear WG2 by meshing with the second screw gear WG2. And a gear HG2.

  Here, with respect to the second worm gear G2, a thrust force Fg is generated in a direction to make the valve body 3 approach the other end wall 11c when the third discharge port E3 is closed (see FIG. 11), and the third discharge. At the time of opening the outlet E3, a thrust force Fg is generated in a direction to separate the valve body 3 from the other end wall 11c side of the valve body accommodation portion 13 (see FIG. 12).

  Hereinafter, a specific operating state of the flow control valve CV will be described based on FIG. In addition, in the said description, while showing about the 1st-3rd opening part M1-M3 of the valve body 3 with a broken line in FIG. 10, it hatches about the 1st-3rd discharge ports E1-E3 of the 1st housing 11. By displaying the state where the two E1 to E3 and M1 to M3 are polymerized and communicating with each other, the relative distinction between the discharge ports E1 to E3 and the openings M1 to M3 is provided for convenience. Shall be

  That is, according to the driving state of the vehicle, the flow control valve CV is driven and controlled by the control current from the electronic controller (not shown) that is calculated and output based on the driving state of the vehicle. The rotational position (phase) of the valve 3 is controlled so that the relative relationship between the discharge ports E1 to E3 and the openings M1 to M3 is as follows.

  In the first state shown in FIG. 10A, all of the first to third openings M1 to M3 are in a non-communicating state with the discharge ports E1 to E3. Thus, in the first state, the cooling water is not supplied to any of the heating heat exchanger HT, the oil cooler OC, and the radiator RD.

  After the first state, in the second state shown in FIG. 10B, only the first opening M1 is in the communication state, and the second and third openings M2 and M3 are in the non-communication state. Thereby, in the second state, the cooling water is supplied only to the heating heat exchanger HT from the first discharge port E1 through the first pipe L1 based on the communication state, and the first discharge port E1 and the first The supply amount changes based on the polymerization amount with the opening M1.

  After the second state, in the third state shown in FIG. 10C, only the third opening M3 is in the non-communicating state, and the first and second openings M1 and M2 are in the communicating state. Accordingly, in the third state, the heating heat exchanger HT and the oil cooler OC are respectively transmitted from the first and second discharge ports E1 and E2 through the first and second pipes L1 and L2 based on the communication state. Cooling water is supplied, and the supply amount changes based on the polymerization amount of the first and second outlets E1 to E2 and the first and second openings M1 to M2.

  After the third state, in the fourth state shown in FIG. 10D, all of the first to third openings M1 to M3 are in communication with the discharge ports E1 to E3. Thus, in the fourth state, cooling water is supplied to all of the heating heat exchanger HT, the oil cooler OC, and the radiator RD, and the first to third outlets E1 to E3 and the first to third openings are provided. The supply amount changes based on the polymerization amount with the parts M1 to M3.

  Hereinafter, characteristic effects and advantages of the flow control valve CV according to the present embodiment will be described based on FIG. 11 and FIG.

  That is, in the conventional flow rate control valve, as in the case of the first and second openings M1 and M2 in the flow rate control valve CV, the biasing force of the elastic member (spring) is applied to all seal members. Thus, the sealability is secured by pressing against the outer peripheral wall of the rotor. Therefore, if it is attempted to increase the biasing force of the elastic member in order to improve the sealing performance at each discharge port, the sliding resistance of the rotor is also increased along with the biasing force, resulting in the deterioration of the rotor's operability. There was a risk of

  On the other hand, in the flow control valve CV, when the third discharge port E3 is closed in which the amount of polymerization of the third opening M3 with respect to the third discharge port E3 is reduced based on the configuration of the second worm gear G2, FIG. As shown by a thick arrow in (a), the thrust force Fg acts in the direction in which the valve body 3 approaches the other end wall 11 c of the valve body accommodation portion 13, as shown in FIG. The third seal member S3 comes in pressure contact with the valve body 3 (third seal sliding contact portion D3), and improves the sealing performance between the third discharge port E3 and the third opening M3 at the time of the valve closing. Can.

  Thereafter, when the valve closed state continues, the water pressure Fw of the cooling water flowing through the inner peripheral side passage 17 acts on the inner surface of the other end wall 3d of the valve body 3 to cause the valve to move by the water pressure Fw. The body 3 is urged to the other end side, and the state in which the other end wall 3d (the third seal sliding surface D3) is in pressure contact with the third seal member S3 is maintained. As a result, high sealing performance can be achieved between the third outlet E3 and the third opening M3 even while the valve body 3 is stationary and the valve closing state in which the thrust force Fg is not generated by the speed reduction mechanism 5 continues. Maintained.

  On the other hand, when the third discharge port E3 is opened to increase the amount of polymerization of the third opening M3 relative to the third discharge port E3, as shown by the thick arrows in FIG. By the thrust force Fg acting in the direction of separating from the other end wall 11c of the portion 13, as shown in FIG. 12 (b), to the valve body 3 (third seal sliding contact portion D3) of the third seal member S3. Unnecessary close contact is suppressed, and the rotational torque of the valve 3 at the time of the valve opening can be reduced.

  As described above, according to the flow control valve CV according to the present embodiment, the valve body 3 is brought into pressure contact with the third seal member S3 by the thrust force Fg at the time of valve closing where sealing is required. It is possible to secure a relatively higher sealability than at the time of valve opening, and the sealability of the third seal member S3 can be improved while securing good operability of the valve body 3.

  On the other hand, at the time of valve opening which does not require sealing, by separating the valve body 3 from the third seal member S3 by the thrust force Fg, it is possible to reduce the sliding resistance of the valve body 3 compared to the valve closing time. The operability of the valve body 3 can be further improved. As a result, it is possible to more effectively achieve both the securing of the good operability of the valve body 3 described above and the improvement of the sealability of the third seal member S3.

  Moreover, the thrust force Fg is automatically generated in the second worm gear G2 which constitutes a drive mechanism necessary for transmission of the drive force of the electric motor 4. For this reason, it is not necessary to add another structure separately in order to generate the thrust force Fg, and securing the good operability of the valve body 3 and the sealability of the third seal member S3 with a relatively simple structure. Coexistence with the improvement of the

  Further, in other words, by utilizing the thrust force Fg, the biasing means for biasing the third seal member S3 used conventionally can be eliminated and it can be constituted by only the third seal member S3. As a result, the number of parts of the flow control valve CV can be reduced, which can contribute to the improvement of the productivity of the flow control valve CV and the reduction of the manufacturing cost.

  Furthermore, in the flow control valve CV, the third seal member S3 is disposed in the axial direction with respect to the valve body 3, so unlike the other discharge ports E1, E2 and the seal members S1, S2, the third discharge port It is not necessary to set the E3 and the third seal member S3 in a substantially circular shape, and the design freedom is improved. In particular, in the present embodiment, the amount of polymerization with the third opening M3 in the third discharge port E3 as described above is gradually changed by setting the third discharge port E3 and the seal member S3 in a substantially fan shape. It is possible to control the discharge amount of the cooling water according to the operating condition of the vehicle.

  In addition, in the flow control valve CV, the first and second discharge ports E1 and E2 are provided to communicate with each other in the radial direction of the valve body accommodation portion 13, and the first and second discharge ports E1 and E2 and the valve Since the first and second seal members S1 and S2 are disposed between the body 3 and in the radial direction, the axial control of the flow control valve CV can be miniaturized as compared with the case where all of them are disposed in the axial direction. .

  Further, a support projection 3e is provided in a substantially central portion on the other end side of the valve body 3 and a bearing hole 11f corresponding to the support projection 3e is recessed in an inner side surface of the other end wall 11c of the valve body accommodating portion 13. By providing, it is provided for the stable rotational support of the other end side of the valve body 3 which is not connected to the rotating shaft 2, and the good operability of the valve body 3 can be secured.

  Furthermore, in the present embodiment, by configuring the reduction mechanism 5 with the first and second worm gears G1 and G2 that are two worm gears, the reduction ratio is increased while suppressing an increase in the projection area of the reduction mechanism 5. It is possible to suppress the increase in size of the flow control valve CV accompanying the increase in the reduction ratio.

  Moreover, by configuring the reduction mechanism 5 with the plurality of worm gears G1 and G2 as described above, a reduction ratio calculation formula ((number of teeth of the first helical gear HG1 / number of teeth of the first screw gear WG1) × (the number of teeth of the second helical gear HG2 / the number of teeth of the second screw gear WG2) can be set to “1” as the denominator of the first and second screw gears WG1, WG2 And there is an advantage that a larger reduction ratio can be obtained.

  The present invention is not limited to the configuration according to the embodiment, and for example, the outer shape of the valve body 3, the size and arrangement of the first to third discharge ports E1 to E3, and the first to third openings M1 to The technical effects of the present invention also apply to the technical features of the present invention such as the generation cause of the thrust force Fg as well as to the specific configuration not directly related to the technical features of the present invention such as the shape, number and arrangement of M3. If it is a form which can be exhibited, it can be freely changed according to the specification etc. of flow control valve CV.

  In particular, the cause of generation of the thrust force Fg is not limited to the reduction mechanism 5 illustrated in the embodiment, and any form may be used as long as the thrust force Fg can be generated. .

  Furthermore, in the embodiment described above, the reduction gear mechanism 5 which is one aspect of the drive mechanism according to the present invention has been illustrated and described, but it is also possible to adopt a speed increase mechanism which is another aspect of the drive mechanism.

  In addition, although a worm gear is adopted in the present embodiment also for the specific configuration of the reduction mechanism 5, the present invention is not limited to the worm gear, and any configuration may be used as long as it can generate the thrust force Fg such as a helical gear. It may be

  Moreover, although application to the circulating system of cooling water was illustrated as an example of application of the flow control valve CV in each of the above-mentioned embodiments, the flow control valve CV is not limited to cooling water, but various types such as lubricating oil etc. It goes without saying that the invention is applicable to various fluids.

3 ... valve body 10 ... introduction port 11, 12 ... first and second housing (housing)
13 ... valve body accommodating portion E3 ... third discharge port (axial direction discharge port)
M3 ... third opening (axial opening)
S3 ... Third seal member (axial direction seal member)

Claims (4)

Hollow valve body accommodating portion is provided, a housing having an inlet to be subjected to introduction of fluid into the valve body accommodating portion, and a discharge outlet that Kyosu the discharge of fluid in the valve body accommodating portion,
A radial opening rotatably supported in the housing , opening in a radial direction with respect to the rotation axis, and an opening area changing in accordance with the rotational position, and an axial opening changing the opening area in accordance with the rotational position part have a, in accordance with the rotational position, a valve body for a fluid introduced from the inlet port to change the amount of discharged to the discharge port,
An axial seal member disposed axially between the housing and the valve body and sealing between the valve body storage portion and the axial opening ;
An actuator that outputs a rotational force,
It is constituted by meshing of gears including a bevel gear, decelerates the rotation by the actuator and transmits it to the valve body, and a thrust force generated by meshing of the bevel gear causes an axial force to be applied to the valve body. The speed reduction mechanism to give
Equipped with
The axial sealing member and the mating member are brought into pressure contact with each other when the helical gear in the speed reduction mechanism is rotated in the direction in which the opening area of the axial opening decreases with the drive of the actuator. When an axial force is applied in the direction to rotate in a direction in which the opening area of the axial opening increases, an axial force acts in a direction in which the mating member separates from the axial seal member. flow control valve, characterized in that there. The flow control valve according to claim 1, wherein the speed reduction mechanism has a worm gear . The flow control valve according to claim 1 , wherein the axial seal member has an elastic force . The flow control valve according to claim 1 , wherein the axial seal member is fixed to the housing .

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