JP6497189B2 - Fluid control valve - Google Patents

Description

  The present invention relates to a fluid control valve capable of blocking the flow of fluid.

  2. Description of the Related Art Conventionally, for example, a flow control valve disposed in a flow path between an engine and a heater core among flow paths through which engine coolant is circulated by a pump is known (see, for example, Patent Documents 1 and 2). The fluid control valve includes a valve body that moves along the direction opposite to the direction of flow of the cooling water when the valve is closed.

  The fluid control valve of Patent Document 1 includes a piston that moves by energizing a solenoid part, a piston cover that houses the piston, and a cylinder that covers the piston cover, and a valve body is integrally formed at the tip of the piston. A cylindrical space with a slight gap is formed between the piston cover and the cylinder, and a communication hole capable of communicating with the cylindrical space is formed in the piston cover. When the valve body is closed, the cooling water on both sides of the piston with respect to the moving direction flows through the communication hole and the cylindrical space, thereby forming an orifice mechanism that increases the fluid pressure acting on the piston. Yes.

  The fluid control valve of Patent Document 2 includes a valve seat formed on the end face of the solenoid portion, and an urging mechanism that separates the valve body from the valve seat when the solenoid portion is not energized, and when the solenoid portion is energized. The valve body is adsorbed by the valve seat and closes. Patent Document 2 describes that in order to stop the flow of the cooling water to the heater core during the warm-up operation, the solenoid is energized to close the valve body before the pump is operated.

JP-A-62-209282 JP 2014-101943 A

  In the conventional flow control valve, when the valve is closed, the valve body moves along the direction opposite to the flow direction of the cooling water, so that a large driving force of the solenoid portion that opposes the fluid pressure of the cooling water is required. . In particular, when configuring an orifice mechanism that increases fluid pressure, such as the flow control valve described in Patent Document 1, it is necessary to further increase the driving force of the solenoid unit. As a result, the solenoid portion is increased in size, and the manufacturing cost and power consumption increase.

  On the other hand, like the flow control valve described in Patent Document 2, when the valve body is closed before the pump is operated, that is, when the fluid pressure of the cooling water does not act, the driving force of the solenoid portion can be reduced. it can. However, in order to close the valve element in the open state by operating the pump, it is necessary to temporarily stop the pump. As a result, it takes time until the driving force of the solenoid part exceeds the inertial force for maintaining the circulation of the cooling water. For this reason, there is room for improvement in realizing quick valve closing.

  Therefore, there is a need for a fluid control valve that can be quickly closed while reducing the size of the apparatus.

  The fluid control valve according to the present invention includes a fluid chamber including a housing having an inlet for receiving a fluid and an outlet for discharging the fluid, and including a first opening through which the fluid flows. A second opening for allowing fluid to flow through the wall between the inside and the outside of the fluid chamber, and an open state in which the second opening is fully opened by rotation, and a throttle state in which the second opening is squeezed A first valve body that can be switched to, a drive unit that rotates the first valve body, and a downstream of the first valve body in the fluid flow direction, and the first valve body is in an open state A second valve body that is opened by a first pressure of a fluid that circulates at a time and is closed by a biasing member that opposes a second pressure of the fluid that circulates when the first valve body is in a throttle state; Is housed in the housing.

  According to this configuration, the first valve body has the second opening formed in the wall portion of the fluid chamber including the first opening through which the fluid is circulated, and the second opening is brought into a throttled state by the rotation of the first valve body. Become. That is, the first valve body rotates along the circumferential direction that is perpendicular to the flow direction, not the direction that opposes the flow direction of the fluid. For this reason, the influence of the fluid pressure that hinders the movement of the first valve body is reduced, and the driving force of the driving unit can be reduced as compared with the prior art. Therefore, the drive unit can be made compact, and the manufacturing cost and power consumption can be saved.

  Moreover, if the flow volume of the fluid which goes to the 2nd valve body is reduced with the throttle state of a 1st valve body like this structure, a 2nd valve body will be closed quickly by an urging member. For this reason, unlike the prior art, when closing from the open state, there is no inconvenience that the valve closing operation is delayed due to the inertial force to maintain the fluid flow. And since the flow volume which goes to a 2nd valve body falls, even when there is much flow volume which flows in into an inflow port, the distribution | circulation of the fluid can be interrupted | blocked reliably by the 2nd valve body.

  Thus, a fluid control valve that can be quickly closed while reducing the size of the apparatus can be provided.

  Another characteristic configuration is that the drive unit includes a spring that biases the first valve body in the opening direction, and a solenoid unit that rotates the first valve body in the throttle direction when energized.

  According to this configuration, when the solenoid portion is energized, the first valve body rotates in the throttle direction against the urging force of the spring. On the other hand, when the solenoid portion is de-energized, it rotates in the opening direction by the biasing force of the spring. In this way, when the rotation of the first valve body is controlled, the solenoid unit only needs to be driven when the fluid control valve is closed, so that power consumption can be saved.

  Another characteristic configuration is that the peripheral wall of the fluid chamber is provided with an even number of the second openings that are symmetrical with respect to the rotation axis.

  If the second openings are arranged symmetrically on the peripheral wall of the fluid chamber as in this configuration, the fluid resistance acts evenly on the first valve body, so that the first valve body is less likely to shake. In addition, when the first valve body transitions from the open state to the throttle state, an inertial force that tries to maintain fluid flow acts around the second opening, but the inertial force between the opposing second openings is Since they cancel each other, the rotation of the first valve body becomes smooth. As a result, the solenoid part can be made more compact.

  Another characteristic configuration is that the sum of the channel cross-sectional areas of the second openings is set to be greater than or equal to the channel cross-sectional area of the inlet.

  If the flow passage cross-sectional area of the second opening is set to be equal to or larger than the flow passage cross-sectional area of the inlet as in this configuration, the orifice mechanism is not constituted by the second opening when the first valve body is open. The fluid pressure does not increase. As a result, the first valve element can be smoothly rotated.

  Another characteristic configuration is that a gap is formed between the peripheral wall and the housing.

  If a gap is provided between the peripheral wall of the first valve body and the housing as in this configuration, it is difficult to receive sliding resistance from the housing when the first valve body rotates. Therefore, the first valve body can be smoothly rotated.

  Another characteristic configuration is that the even number of the second openings are inclined in the same direction with respect to the radial direction of the peripheral wall.

  If all the second openings are inclined in the same direction as in this configuration, the fluid discharged from the second openings forms a spiral flow. That is, the fluid discharged from the second opening in the peripheral wall is not diffused but is concentrated toward the outlet, and the fluid flowing through the fluid control valve is smoothly distributed. As a result, for example, when used as a fluid control valve for engine cooling, pump loss can be reduced.

It is a schematic diagram of the cooling system which has arrange | positioned the fluid control valve. It is sectional drawing of a fluid control valve when a 1st valve body is opened. It is sectional drawing of a fluid control valve when a 1st valve body is opened. It is the IV-IV line arrow directional view of FIG. FIG. 5 is a view taken along line VV in FIG. 2. FIG. 6 is a view taken along line VI-VI in FIG. 3. It is a perspective view which shows a 2nd housing. It is a perspective view which shows a 4th housing. It is a perspective view which shows a yoke part. It is a perspective view which shows a 1st valve body. It is explanatory drawing which shows rotation of a 1st valve body. It is sectional drawing of the 1st valve body which concerns on another Embodiment 1, and a 2nd housing. It is sectional drawing of the fluid control valve which concerns on another Embodiment 2.

  Hereinafter, embodiments of a fluid control valve according to the present invention will be described with reference to the drawings. In the present embodiment, an example of the fluid control valve will be described as a fluid control valve V used in a cooling system for an engine E for an automobile. However, the present invention is not limited to the following embodiments, and various modifications can be made without departing from the scope of the invention.

  As shown in FIG. 1, the cooling system of the engine E is cooled between the engine E and the heater core H, and the first circulation path 1 that circulates cooling water (an example of fluid) between the engine E and the radiator R. A second circulation path 2 that circulates water and a water pump P that supplies cooling water to the engine E are provided.

  Outflow passages of cooling water from the radiator R and the heater core H in the first circulation passage 1 and the second circulation passage 2 are connected to the water pump P via the thermostat valve 3. In the first circulation path 1, the cooling water heated by the engine E is cooled by the radiator R and then returned to the engine E through the thermostat valve 3. In the second circulation path 2, a fluid control valve V is disposed between the engine E and the heater core H, and when the fluid control valve V is in an open state, the cooling water heated by the engine E is used as air in the passenger compartment. Is allowed to flow into the heater core H that warms the heater. At this time, the cooling water cooled by heat exchange by the heater core H is returned to the engine E through the thermostat valve 3.

  On the other hand, when the cooling water is lower than a predetermined temperature, the fluid control valve V is closed to prevent the temperature of the cooling water from being lowered due to heat exchange of the heater core H. When the temperature of the cooling water is low, the thermostat valve 3 is also closed, so that the cooling water does not circulate to the radiator R. For this reason, the temperature rise of the cooling water during the warm-up operation of the engine E can be promoted, and the fuel efficiency can be improved.

(Basic configuration)
As shown in FIG. 2, the fluid control valve V includes a housing 4 having an inlet 41a for receiving cooling water and an outlet 44a for discharging cooling water, and a fluid chamber 53 including a first opening 53a for circulating the cooling water. A first valve body 5, a drive unit K that rotates the first valve body 5, and a second valve body 6 that is disposed downstream of the first valve body 5 in the flow direction of the cooling water. ing. The first valve body 5, the drive unit K, and the second valve body 6 are accommodated in the housing 4. In the present embodiment, the housing 4 is made of a resin material, and the first valve body 5 and the second valve body 6 are made of a magnetic material. In addition, the 2nd valve body 6 may be comprised with a resin material, and only the part which contributes to rotation of the 2nd valve body 6 may be comprised with a magnetic material, and it does not specifically limit.

  Although details will be described later, the drive unit K includes a torsion spring 9 (an example of a spring) that urges the first valve body 5 in the opening direction, and a solenoid that rotates the first valve body 5 in the throttle direction when energized. Part S.

(housing)
The housing 4 includes a first housing 41, a second housing 42, a third housing 43, and a fourth housing 44 in order from the upstream side in the flow direction of the cooling water. The housings 41 to 44 are fixed to each other by adhesion, vibration welding, or the like. In this embodiment, the housing 4 is composed of four members. However, as long as the solenoid part S, the first valve body 5 and the second valve body 6 can be accommodated, the housing 4 is composed of one or more members. You may comprise, It does not specifically limit.

  The first housing 41 is provided with an inlet 41a that receives cooling water in the center and distributes the cooling water to the first opening 53a of the first valve body 5, and a solenoid portion S is disposed around the inlet 41a. In the present embodiment, the solenoid part S is insert-molded with resin inside the first housing 41.

  As shown in FIG. 7, the second housing 42 is formed in a donut shape, and has an inner peripheral portion 42 a into which the valve portion 52 of the first valve body 5 is inserted at the center. As shown in FIG. 2, there is a gap between the inner peripheral portion 42a and the valve portion 52 (the peripheral wall 53b) in a state where the center of the inner peripheral portion 42a is aligned with the rotation axis X of the first valve body 5. Is formed. In addition, as shown in FIG. 4, the inner peripheral portion 42 a has a pair of holes 42 b that are symmetric with respect to the rotation axis X so that the cross-sectional area of the channel increases in the radial direction. A plurality of sets (in this embodiment, two sets of four hole portions 42b) are formed. Furthermore, as shown in FIG. 2, the plurality of hole portions 42 b extend to the third housing 43 along the rotation axis X direction. Thereby, the cooling water discharged from the fluid chamber 53 of the first valve body 5 flows to the second valve body 6.

  Further, as shown in FIG. 7, a locking groove 42 c in which one end of the torsion spring 9 is locked and formed is formed on the outer peripheral side of the second housing 42. In the present embodiment, a plurality of the locking grooves 42c are provided along the circumferential direction. However, it is sufficient if there is only one position where the one end of the torsion spring 9 is fixed. Further, the hole 42b of the inner peripheral portion 42a may be extended so that the channel cross-sectional area becomes equal in the outer radial direction without extending the channel cross-sectional area in the outer radial direction. Each hole 42b may be connected in a ring shape, and is not particularly limited.

  As shown in FIGS. 2 and 5, on the center side of the third housing 43, there is a support portion 43 a that supports the valve portion 52 of the first valve body 5, and a support portion 43 a that is smaller in diameter than the support portion 43 a. A columnar portion 43 b protruding toward the second valve body 6 is formed. As shown in FIG. 5, the support portion 43 a is connected to the outer peripheral side of the third housing 43 by four leg portions 43 c that are arranged at positions that do not overlap the hole portion 42 b when viewed in the direction of the rotational axis X. . Further, on the outer peripheral side of the third housing 43, a step portion 43d for guiding the coolant in the direction of the rotation axis X is formed. As shown in FIG. 2, the columnar part 43b and the stepped part 43d function as a valve seat for the second valve body 6, and in contact portions with the second valve body 6 in the columnar part 43b and the stepped part 43d, Annular seal members S1, S2 are provided. The annular seal members S1, S2 may be provided on the second valve body 6 side, or the annular seal members S1, S2 may be omitted.

  As shown in FIG. 2 and FIG. 8, the fourth housing 44 has a second base body 6 and a coil spring 7 (described below as a biasing member), which are described later, on a cylindrical base portion 44b from which a cooling water outlet 44a projects. An accommodation hole 44c for accommodating an example is formed. 44 d of guide protrusions which the 2nd valve body 6 slidably contacts are formed in this accommodation hole part 44c, and six places are arrange | positioned at equal intervals along the circumferential direction. Six outer peripheral grooves 44e through which cooling water can flow are formed between the guide protrusions 44d. By providing the guide protrusion 44d, the sliding contact area between the second valve body 6 and the accommodation hole 44c is reduced, so that the second valve body 6 can be moved smoothly. In addition, it is good also as a structure which abbreviate | omits the outer periphery groove | channel 44e and makes the 2nd valve body 6 slidably contact over the perimeter of the accommodation hole part 44c. Further, the guide protrusions 44d are not limited to six locations, and may be appropriately set at two or more locations.

(Solenoid part)
As shown in FIG. 2, the solenoid part S is housed in the first housing 41 and has a U-shaped cross section in which the coil part Sa wound around the bobbin and the magnetic flux generated from the coil part Sa when energized are transferred. The yoke portion Sb is concentrically provided. As shown in FIG. 9, the yoke portion Sb is formed in a hollow cylindrical shape, and an inflow port 41a is disposed in the inner hollow portion. The yoke portion Sb has a first yoke portion Sb1 having a T-shaped cross section and a cylindrical second yoke portion Sb2, and is configured by fitting the first yoke portion Sb1 and the second yoke portion Sb2. ing. Note that the first yoke portion Sb1 and the second yoke portion Sb2 may be integrally formed, and are not particularly limited.

  A plurality of projecting portions Ta (six in this embodiment) for flowing a magnetic flux toward the first valve body 5 are provided at the distal end (first valve body 5 side) of the second yoke portion Sb2 in the rotation axis X direction. Protruding along. As shown in FIG. 2, if the solenoid part S is insert-molded in the first housing 41, the tip parts of the plurality of protrusions Ta are exposed.

(First disc)
As shown in FIGS. 2 and 10, the first valve body 5 is configured in a bottomed cylindrical shape, and receives a magnetic flux from the solenoid unit S when energized to rotate. 51 and a valve portion 52 that is formed so as to project integrally therewith. In addition, a fluid chamber 53 including a first opening 53 a into which cooling water from the inflow port 41 a flows is formed inside the first valve body 5. Further, as shown in FIG. 2, the first valve body 5 is fixed to the support portion 43 a of the third housing 43 by inserting a pin 55 with the bearing member 54 interposed therebetween. The bearing member 54 and the pin 55 function as a bearing mechanism that stabilizes the rotational posture of the first valve body 5. A bearing mechanism may be provided between the first valve body 5 and the first yoke portion Sb1. In this case, the rotation posture of the first valve body 5 is more stable.

  As shown in FIG. 10, the rotation part 51 is formed with a plurality of rotation protrusions Tb (six in this embodiment) that protrude in the radially outward direction. The other end of the torsion spring 9 whose one end is fixed to the locking groove 42c of the second housing 42 is locked and fixed to one rotating protrusion Tb among the plurality of rotating protrusions Tb. Further, as shown in FIG. 3, the plurality of rotation protrusions Tb face the protrusion Ta of the second yoke portion Sb2 along the rotation axis X direction when the first valve body 5 is in the contracted state. Position.

  As shown in FIG. 10, a plurality of second openings 53 c (four in this embodiment) are formed through the peripheral wall 53 b (wall portion) of the fluid chamber 53 at equal intervals in the circumferential direction. The second opening 53 c allows cooling water to flow through the inside and outside of the fluid chamber 53.

  As shown in FIG. 4, the pair of second openings 53 c are arranged symmetrically with respect to the rotation axis X. That is, an even number of second openings 53 c that are symmetrical with respect to the rotation axis X are provided in the peripheral wall 53 b of the fluid chamber 53. As shown in FIG. 10, the total of the channel cross-sectional areas of the second openings 53c is set to be greater than or equal to the channel cross-sectional area of the inflow port 41a. Thereby, the cooling water discharged | emitted via the 2nd opening 53c from the inflow port 41a distribute | circulates smoothly. As a result, the cooling water does not stay in the fluid chamber 53 and the fluid resistance applied to the second opening 53c is small, so that the first valve body 5 rotates smoothly. The number of the second openings 53c is not limited to an even number so as to be symmetric with respect to the rotation axis X, and one or more asymmetric second openings 53c may be provided.

(Second valve body)
As shown in FIG. 2, the 2nd valve body 6 is arrange | positioned from the 1st valve body 5 in the downstream of the flow direction of cooling water, and is formed in the disk shape. The second valve body 6 is urged upstream in the flow direction by a coil spring 7. The second valve body 6 is formed with a recess 6a in which the coil spring 7 is locked and a discharge hole 6b for discharging the coolant at the center.

(Opening and closing operation of fluid control valve)
As described above, the drive unit K includes the torsion spring 9 that biases the first valve body 5 in the opening direction, and the solenoid unit S that rotates the first valve body 5 in the throttle direction when energized. . That is, the solenoid unit S is normally de-energized, and the solenoid unit S only needs to be energized only when the flow of the cooling water to the heater core H is interrupted, for example, during warm-up operation. it can.

  As shown in FIGS. 2 and 4, when the solenoid portion S is not energized, the urging force of the torsion spring 9 causes the second opening 53 c of the first valve body 5 and the hole portion 42 b of the second housing 42 to communicate with each other. . That is, the second opening 53c is fully opened. At this time, the cooling water flows in the order of the inlet 41a of the first housing 41, the fluid chamber 53 of the first valve body 5, the second opening 53c, the hole 42b, and the stepped portion 43d of the third housing 43, A fluid pressure (first pressure) acts on the second valve body 6. When the first pressure exceeds the urging force of the coil spring 7, the second valve body 6 is opened, and the coolant is discharged from the discharge hole 6 b of the second valve body 6 and the outer peripheral groove 44 e of the fourth housing 44. Circulates from the outlet 44a of the fourth housing 44 to the heater core H via the.

  On the other hand, as shown in FIG. 11, when the solenoid portion S is energized, a magnetic flux flows from the projection Ta of the second yoke portion Sb2 toward the first valve body 5, and the rotation projection Tb of the first valve body 5 It is attracted to the protrusion Ta. As a result, as shown in FIGS. 3 and 6, the first valve body 5 rotates and the second opening 53 c of the first valve body 5 and the hole 42 b of the second housing 42 are displaced in the radial direction. Arrangement. At this time, since a gap is formed between the valve portion 52 of the first valve body 5 and the inner peripheral portion 42a of the second housing 42, a small amount of cooling water passes through the gap from the second opening 53c. The hole 42b and the stepped portion 43d of the third housing 43 are distributed in this order. That is, it is a throttle state that squeezes the second opening 53c. Since the fluid pressure (second pressure) of the leaked cooling water is significantly lower than the first pressure, the urging force of the coil spring 7 acting on the second valve body 6 exceeds the second pressure, and the second valve body 6 Closes quickly.

  In this way, the pressure of the cooling water toward the second valve body 6 is reduced by the throttle operation of the first valve body 5, and the coil spring 7 counteracts the pressure to close the second valve body 6 to cool the cooling water. Block the distribution of In the present embodiment, since the first valve body 5 is turned to the throttle state, the turning direction of the first valve body 5 is perpendicular to the flow direction of the cooling water. For this reason, the influence of the fluid pressure that hinders the rotation of the first valve body 5 is reduced, and the driving force of the solenoid unit S can be reduced. Therefore, the solenoid part S can be made compact and manufacturing cost and power consumption can be saved. Moreover, since the 2nd valve body 6 is closed in the state which reduced the pressure of the cooling water, the 2nd valve body 6 is closed quickly and responsiveness is high. Moreover, since the amount of cooling water flowing through the second valve body 6 is very small, the flow of cooling water can be reliably blocked.

  Further, in the present embodiment, since the second opening 53 c that is symmetric with respect to the rotation axis X is provided in the peripheral wall 53 b of the fluid chamber 53 of the first valve body 5, the first valve body 5 is cooled. Water flow resistance acts equally. As a result, even when the first valve body 5 is supported only by the bearing member 54, the shaft shake of the first valve body 5 can be prevented. Further, when the first valve body 5 shifts from the open state to the throttled state, an inertial force that tries to maintain the circulation of the cooling water acts on the periphery of the second opening 53c. The inertia forces cancel each other. In addition, since a gap is formed between the valve portion 52 of the first valve body 5 and the inner peripheral portion 42a of the second housing 42, the first valve body 5 receives a sliding resistance from the second housing 42. hard. As a result, the first valve body 5 can be smoothly rotated, and the driving force of the solenoid portion S can be further reduced.

  Hereinafter, another embodiment will be described. Since the basic configuration is the same as that of the above-described embodiment, only different configurations will be described with reference to the drawings. In addition, in order to make an understanding of drawing easy, it demonstrates using the same member name and code | symbol as embodiment mentioned above.

[Another embodiment 1]
In the embodiment described above, the even number of second openings 53 c of the first valve body 5 and the even number of holes 42 b of the second housing 42 are provided along the radial direction of the peripheral wall 53 b of the first valve body 5. Instead, as shown in FIG. 12, the even number of second openings 53 c of the first valve body 5 and the even number of holes 42 b of the second housing 42 are arranged in the radial direction of the peripheral wall 53 b of the first valve body 5. May be inclined in the same direction. In this case, the cooling water discharged from the second opening 53c of the peripheral wall 53b forms a spiral flow. That is, the cooling water discharged from the second opening 53 c is collected so as to go in the direction of the rotation axis X, and goes toward the discharge hole 6 b of the second valve body 6. As a result, the flow of the cooling water passing through the fluid control valve V becomes smooth, and the pump loss of the water pump P can be reduced. Note that the even number of second openings 53c of the first valve body 5 and the even number of holes 42b of the second housing 42 may be inclined in the same direction with respect to the rotation axis X direction.

[Another embodiment 2]
In the embodiment described above, the second opening 53 c of the first valve body 5 is provided in the peripheral wall 53 b of the fluid chamber 53. Instead, as shown in FIG. 13, the second opening 53 d may be provided in the bottom wall (wall portion) of the fluid chamber 53. In this case, a plurality of second openings 53d are formed along the circumferential direction so as to surround the bearing member 54 of the first valve body 5, and the first valve is provided in the support portion 43a and the columnar portion 43b of the third housing 43. A plurality of through-hole portions 42e are formed corresponding to the position of the second opening 53d where the body 5 is open. Thereby, the circulation of the cooling water becomes smooth along the direction along the rotation axis X.

In addition, the following technical idea can also be grasped | ascertained from embodiment mentioned above.
(Additional item 1)
The fluid control valve V may form a discharge hole 6 b that discharges fluid at the center of the second valve body 6. With such a configuration, the fluid flowing through the fluid control valve V is as much as possible along the direction of the rotation axis X, so that the pump loss of the water pump P can be reduced.

(Appendix 2)
The fluid control valve V may be provided with annular seal members S1 and S2 on the side of the housing 43 with which the second valve body 6 abuts. With such a configuration, as in the case where the annular seal members S1 and S2 are provided on the second valve body 6 which is a moving body, the disadvantage that the annular seal members S1 and S2 that move are a fluid flow resistance is reduced. Is done. Therefore, the fluid can be smoothly circulated inside the fluid control valve V.

(Additional Item 3)
The fluid control valve V may be formed with a plurality of guide protrusions 44d protruding radially inward on the housing 44 with which the second valve body 6 is in sliding contact. By providing the guide protrusion 44d as in this configuration, the sliding contact area between the second valve body 6 and the housing 44 is reduced, so that the second valve body 6 can be moved smoothly. Therefore, the fluid control valve V can be quickly closed.

(Appendix 4)
In the fluid control valve V, the solenoid portion S includes a yoke portion Sb2 having a protrusion Ta protruding along the rotation axis direction, and the first valve body 5 includes a rotation protrusion Tb protruding in the radially outward direction. The first projecting member 5 may be switched to the throttled state by rotating the first projecting member 5 by turning the projecting projecting member Tb toward the projecting member Ta by energizing the solenoid unit S. As described above, the first valve body 5 can be controlled to rotate with a simple configuration in which the protrusion Ta is provided on the solenoid S and the rotation protrusion Tb is provided on the first valve body 5. Therefore, there is no need to separately provide a motor for rotating the first valve body 5, which is reasonable.

(Appendix 5)
The fluid control valve V may be provided with a plurality of second openings 53 d on the bottom wall of the fluid chamber 53. As a result, the fluid flow becomes smooth along the rotation axis X.

[Other Embodiments]
(1) In the above-described embodiment, when the first valve body 5 is in the throttle state as shown in FIG. 3, the rotation protrusion Tb of the first valve body 5 is the first along the rotation axis X direction. The two yoke portions Sb2 are configured so as to face the protruding portions Ta. Instead of this, the rotation protrusion Tb of the first valve body 5 may be configured to face the protrusion Ta of the second yoke part Sb2 in the radial direction. That is, the rotation part 51 of the first valve body 5 is arranged on the inner side of the second yoke part Sb2 in a state where the protrusion Ta of the second yoke part Sb2 is further protruded in the rotation axis X direction. .
(2) In the above-described embodiment, six rotation protrusions Tb of the first valve body 5 and six protrusions Ta of the second yoke part Sb2 are provided. However, one or more than two may be used. .
(3) In the above-described embodiment, the urging force of the torsion spring 9 is used when the first valve body 5 is opened, but other urging members such as a leaf spring may be used. Similarly, the biasing member that biases the second valve body 6 is not limited to the coil spring 7.
(4) The fluid control valve V is not limited to use in the cooling system of the engine E for automobiles, and may be used in an engine oil circulation system.

  INDUSTRIAL APPLICABILITY The present invention can be used for a fluid control valve that controls the flow of a fluid such as cooling water or oil of a vehicle.

4 Housing 5 First valve body 6 Second valve body 7 Coil spring (biasing member)
9 Torsion spring (spring)
41a Inlet 44a Outlet 53 Fluid chamber 53a First opening 53b Peripheral wall (wall part)
53c 2nd opening K Drive part S Solenoid part X Rotating shaft

Claims (6)

A housing having an inlet for receiving fluid and an outlet for discharging fluid;
A fluid chamber including a first opening through which fluid is circulated, and a second opening through which fluid is circulated is formed in the wall of the fluid chamber over the inside and outside of the fluid chamber, A first valve body that can be switched between an open state in which the two openings are fully open and a throttle state in which the second opening is squeezed;
A drive unit for rotating the first valve body;
The first valve body is disposed downstream of the first valve body in the fluid flow direction, and is opened by the first pressure of the fluid flowing when the first valve body is in the open state, and the first valve body is in the throttle state. A fluid control valve in which a housing is housed in a second valve body that is closed by an urging member that opposes a second pressure of fluid flowing at a certain time.   2. The fluid control valve according to claim 1, wherein the driving unit includes a spring that biases the first valve body in an opening direction, and a solenoid unit that rotates the first valve body in a throttle direction when energized.   3. The fluid control valve according to claim 1, wherein an even number of the second openings that are symmetrical with respect to the rotation axis are provided on a peripheral wall of the fluid chamber.   The fluid control valve according to claim 3, wherein the total of the cross-sectional areas of the second openings is set to be greater than or equal to the cross-sectional area of the inlet.   The fluid control valve according to claim 3 or 4, wherein a gap is formed between the peripheral wall and the housing.   The fluid control valve according to any one of claims 3 to 5, wherein the even number of the second openings are inclined in the same direction with respect to the radial direction of the peripheral wall.

Images