JP2015218853A - Control valve - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a control valve capable of reducing leak inside a housing.SOLUTION: A control valve 1 includes: a cylindrical housing 10; a pump communication hole provided in the housing 10, and for communicating with a pump; a first communication hole 30 and a second communication hole provided on an inner peripheral wall 12 of the housing 10; a cylindrical rotor 50 accommodated inside the housing 10 coaxially with the housing 10, and having a spreading characteristic in a diameter expanding direction; a rotor rotation mechanism 60 for rotating the rotor 50 along the inner peripheral wall 12 of the housing 10; a first opening part for switching a communication state of the first communication hole 30 and a central space 13 on the radial direction inner side of the rotor 50; a second opening part for switching a communication state of the second communication hole and the central space 13; and a plurality of groove parts 90 formed across the length in an axial direction of the rotor 50 in a region R which the first opening part and the second opening part do not face even when the rotor 50 rotates, out of the inner peripheral wall 12 of the housing 10.

Description

  The present invention relates to a control valve for controlling fluid flow.

  Conventionally, control valves have been used to control fluid flow. As an example of such a control valve, there is one described in Patent Document 1 whose source is shown below.

  Patent Document 1 describes a control valve for a fluid circulation circuit including a body having a fluid inlet and at least two fluid outlets. This control valve rotates an annular seal ring made of a material with a low coefficient of friction to distribute fluid through the fluid outlet. A plurality of spaced apart holes are formed in the surface of the seal ring to reduce a contact area with the side wall of the housing.

JP 2006-512547 A

  If the technique described in Patent Document 1 is used for a cooling passage of an engine mounted on a vehicle, for example, when the engine is in a low rotation state such as idle rotation, the rotation speed of the water pump decreases and the fluid pressure decreases. Therefore, it is conceivable that fluid leaks between the seal ring and the housing. It is also conceivable that fluid leaks from a gap formed between a hole formed in the surface of the seal ring and the side wall of the housing. As a result, for example, when the engine is started, the warm-up of the engine is delayed, and the fuel consumption may be deteriorated.

  In view of the above problems, an object of the present invention is to provide a control valve that can operate smoothly while reducing leakage in the housing.

  In order to achieve the above object, the control valve according to the present invention includes a cylindrical housing, a pump communication hole provided on one end surface in the axial direction of the housing and communicating with a pump, and an inner peripheral wall of the housing. A first communication hole provided in the inner circumferential wall, the second communication hole provided in the inner peripheral wall at a position different from the first communication hole in the axial direction, and the first communication hole and the housing in the housing. A cylindrical rotor that is accommodated on the same axis and has a spreading characteristic in the diameter-enlarging direction; a rotor rotation mechanism that rotates the rotor along the inner peripheral wall of the housing around the axis of the rotor; and the rotor A first opening formed in the rotor, the first opening switching the communication state between the first communication hole and a central space radially inward of the rotor according to rotation of the rotor; The second opening that switches the communication state between the second communication hole and the central space in accordance with the rotation of the rotor, and the first opening even when the rotor rotates among the inner peripheral walls of the housing. And in the area | region which the said 2nd opening part does not oppose, it exists in the point provided with the some groove part formed over the length of the axial direction of the said rotor at least.

  By providing a plurality of wall portions on the inner peripheral wall of the housing in this way, the inner periphery of the rotor and the housing in the region of the inner peripheral wall of the housing where the first opening and the second opening are not opposed when the rotor is rotated. The contact area with the peripheral wall can be reduced. Therefore, the rotor can be easily slid and rotated along the inner peripheral wall of the housing. On the other hand, in the inner peripheral wall of the housing, the vicinity of the first communication hole and the second communication hole is a region where the first opening and the second opening face each other according to the rotation of the rotor, so that no groove is formed. Therefore, in the vicinity of the first communication hole and the second communication hole, the adhesion between the rotor and the inner peripheral wall of the housing can be enhanced by the spreading characteristics of the rotor, so that fluid leaks between the rotor and the housing. Can be prevented. Accordingly, it is possible to reduce fluid leakage in the housing.

  Moreover, it is preferable that the cross-sectional shape of the groove is a triangle.

  In general, when two flat plates are slightly inclined from a parallel state and are arranged with a narrow gap, and the gap is filled with fluid, when the two flat plates move relative to each other, the fluid is narrowed accordingly. It is known that the pressure in the gap increases by being dragged into the gap. If it is set as the said structure, a rotor can be floated from a housing using such a pressure, and a frictional force can be reduced. Therefore, since the rotor and the inner peripheral wall of the housing can be brought into non-contact when the rotor is rotated, the sliding resistance can be reduced and the rotor can be easily rotated when the rotor is rotated.

  In addition, it is preferable that the groove portion has a cross-sectional area that is narrower toward the downstream side in the flow direction of the fluid flowing along the inner peripheral wall of the housing.

  When the fluid flows through the groove, the pressure increases as the width of the groove increases, and the pressure decreases as the width of the groove decreases. Therefore, by gradually narrowing the groove width along the fluid flow direction, a flow of fluid is formed in the groove due to the pressure difference, and even if foreign matter is mixed in the fluid, It is possible to prevent clogging with foreign substances.

  Further, it is preferable that the groove portion is formed in parallel with the axis of the housing.

  With such a configuration, it is possible to minimize the length of the groove portion from the one end portion in the axial direction of the rotor to the other end portion. Therefore, even when the foreign matter mixed in the fluid enters the groove portion, the foreign matter can be easily discharged from the groove portion.

  In addition, a sealing surface that is in liquid-tight contact with the rotor is formed in a region of the inner peripheral wall of the housing where the first opening and the second opening face when the rotor rotates. It is preferable.

  With such a configuration, fluid leakage (intrusion) between the outer peripheral surface of the rotor and the inner peripheral wall of the housing can be prevented within the movement range of the first opening and the second opening.

  In addition, it is preferable that the rotor is configured to reduce spreading characteristics in the diameter-expanding direction at a high temperature.

  For example, the rotation of the rotor may be performed using a motor. In such a motor, the winding resistance of the coil of the motor increases at a high temperature, and no current can flow, so the output torque of the motor decreases. For this reason, when the environmental temperature in which the motor is used changes, a motor having a large rated output is generally selected in consideration of the output torque required at a high temperature, which increases the cost. According to this configuration, since the spreading characteristic of the rotor is reduced at high temperatures, the sliding resistance with respect to the inner peripheral wall of the rotor housing can be reduced, and an inexpensive motor with a small rated output can be used. .

  Further, it is preferable that the rotor is configured by bonding materials having different thermal expansion coefficients to the inner peripheral surface side and the outer peripheral surface side.

  With such a configuration, the material on the outer peripheral surface side expands in the circumferential direction at high temperatures, so that the material on the inner peripheral surface side receives a load in the diameter reducing direction, and the rotor can be reduced in diameter. For this reason, since the deformation of the rotor at a high temperature can be promoted, the sliding resistance against the inner peripheral wall of the rotor housing can be reduced. Therefore, the rotor can be easily rotated.

  Further, it is preferable that the rotor is configured to be deformed from the inner peripheral wall of the housing to a separated state when the rotor is in a temperature higher than a predetermined use temperature range.

  With such a configuration, when the rotor is heated excessively, the diameter of the rotor is reduced, and the pressing force of the rotor against the inner peripheral wall of the housing becomes zero. In this case, fluid pressure acts on the rotor, and the rotor is separated from the inner peripheral wall of the housing. Therefore, regardless of the positions of the first opening and the second opening, the first communication hole, the second communication hole, and the central space can be in communication with each other, so that the fluid is blocked by the control valve. Can be prevented.

It is an example of the cooling circuit provided with the control valve. It is a perspective view of a control valve. It is a perspective view of a rotor. It is a figure which shows the state which extended the rotor shown by FIG. 3 to flat form. It is sectional drawing in the VV line of FIG. It is sectional drawing in the VI-VI line of FIG. It is a figure used for description of pressure distribution of a crevice. It is the figure which showed typically the temperature dependence of a rotor, and the state of the control valve by predetermined temperature.

  The control valve according to the present invention is configured to be able to control fluid flow while reducing fluid leakage in the housing. Hereinafter, the control valve 1 of the present embodiment will be described. FIG. 1 shows an example in which the control valve 1 is employed in a cooling circuit 100 that cools the engine of a vehicle, and FIG. 2 shows a perspective view of the control valve 1.

  The vehicle cooling circuit 100 shown in FIG. 1 has a first path 2 and a second path 3. The first path 2 is a path through which the refrigerant (fluid) from the engine 4 circulates through the radiator 5, and the second path 3 is a path through which the refrigerant from the engine 4 circulates through the heater core 6. In both paths, the refrigerant is circulated by the pump 7. A control valve 1 is provided on the upstream side of the pump 7, and the control valve 1 is configured to allow refrigerant to flow from each of the radiator 5 and the heater core 6.

  As shown in FIG. 2, the control valve 1 includes a housing 10, a pump communication hole 20, a first communication hole 30, a second communication hole 40, a rotor 50, a rotor rotating mechanism 60, a first opening 70, and a second opening. A portion 80 and a groove portion 90 (see FIG. 5) are provided. The housing 10 is configured in a cylindrical shape. In the present embodiment, the housing 10 is configured in a cylindrical shape. Although details will be described later, a pump communication hole 20 is attached to the top surface 11 of the housing 10, and a rotor rotation mechanism 60 is attached to the bottom surface 14. The housing 10 can be configured using a metal, or can be configured using a resin.

  The pump communication hole 20 is provided on one axial end surface of the housing 10 and communicates with the pump 7. One end surface in the axial direction of the housing 10 is one of two surfaces (the top surface 11 and the bottom surface 14) orthogonal to the axial direction of the tube among the surfaces of the cylindrical housing 10. In the example of FIG. 2, the top surface 11 corresponds. As shown in FIG. 1, the pump communication hole 20 is used as the first path 2 and the second path 3 and is connected to the pump 7.

  The first communication hole 30 and the second communication hole 40 are provided in the inner peripheral wall 12 of the housing 10. The inner peripheral wall 12 of the housing 10 is an inner wall parallel to the axial center of the cylindrical housing 10 among the inner walls of the cylindrical housing 10. In the present embodiment, as shown in FIG. 2, the first communication hole 30 and the second communication hole 40 coincide with each other in the circumferential direction of the housing 10 and are provided at different positions in the axial direction. That is, when the housing 10 is viewed from the outside in the axial direction, the first communication hole 30 and the second communication hole 40 overlap in the axial direction, and when the housing 10 is viewed from the outside in the radial direction, the first communication hole is formed. The hole 30 and the second communication hole 40 are provided so as to be separated from each other. For ease of understanding, FIG. 2 will be described on the assumption that the first communication hole 30 is provided on the top surface 11 side and the second communication hole 40 is provided on the bottom surface 14 side.

  The rotor 50 is accommodated in the housing 10 coaxially with the housing 10. The rotor 50 is configured according to the shape of the cylindrical space formed on the radially inner side of the housing 10. The cylindrical space is a space surrounded by the inner peripheral wall 12 of the cylindrical housing 10. In this embodiment, since the housing 10 is formed in a cylindrical shape, the rotor 50 is also formed in a cylindrical shape. Such a rotor 50 is formed, for example, by rolling a plate-like resin of a grade (sliding grade) excellent in slidability such as polytetrafluoroethylene (PTFE) into a cylindrical shape, and the shaft center of the rotor 50 is a housing. The housing 10 is accommodated in the cylindrical space so as to contain the rotor 50 so as to coincide with the axis of the shaft 10.

  Further, the rotor 50 is formed in a cylindrical shape having spreading characteristics in the diameter expanding direction. Such a cylindrical rotor 50 is shown in FIG. The diameter increasing direction refers to a direction in which the inner diameter of the cylindrical rotor 50 increases. For this reason, having the spreading characteristic in the diameter-expanding direction means having the characteristic that the inner diameter of the cylindrical rotor 50 is increased.

  The rotor 50 having such spreading characteristics is preferably configured to have an axial opening 53 that opens from one end in the axial direction to the other end. Opening from one end portion in the axial direction to the other end portion means that the rotor 50 has a gap uniformly along the axial direction. That is, the rotor 50 means that the cross section of the rotor 50 intersecting in the axial direction is formed in a “C shape”. Accordingly, the axial opening 53 is configured to have the same length as the axial length of the rotor 50. Thereby, the rotor 50 which has a spreading | diffusion characteristic can be comprised easily by rounding a plate-shaped material to a cylinder shape.

  A first opening 70 and a second opening 80 are formed in the rotor 50. The first opening 70 switches the first communication hole 30 and the central space 13 to the communication state according to the rotation of the rotor 50, and the second opening 80 changes the second communication hole 40 and the central space according to the rotation of the rotor 50. 13 is switched to the communication state. The first opening 70 corresponds to a hole formed in the rotor 50, and the central space 13 corresponds to a space inside the rotor 50 in the radial direction. The first opening 70 switches the first communication hole 30 and the central space 13 to the communication state or the blocking state according to the rotation of the rotor 50. The second opening 80 corresponds to a hole formed in the rotor 50, and switches the second communication hole 40 and the central space 13 to a communication state or a blocking state according to the rotation of the rotor 50.

  In the present embodiment, the first opening 70 and the second opening 80 are configured so that three states can be set. FIG. 4 shows a state in which the rotor 50 is flattened so that the three states can be easily understood. The three states are the state A in which the first communication hole 30 and the central space 13 are in communication with each other, the state A in which the second communication hole 40 and the central space 13 are in communication, and the first communication hole 30 and the central space 13. Are closed, and the second communication hole 40 and the central space 13 are in communication with each other, the first communication hole 30 and the central space 13 are blocked, and the second communication hole 40 and the central space 13 are connected. It is configured to be switchable to any one of the state C in which the space 13 is shut off.

  Therefore, as shown in FIG. 4, in the state A, both the first opening 70 and the second opening 80 are opened, and in the state B, only the second opening 80 is opened. In the state C, the first opening 70 and the second opening 80 are not opened. Therefore, the rotor 50 includes a portion where the first opening 70 and the second opening 80 overlap, a portion where only the second opening 80 is provided, and the first opening when the rotor 50 is viewed in the axial direction. And a portion where both the portion 70 and the second opening 80 are not provided. Thereby, it is possible to control the flow of the fluid in each of the first path 2 and the second path 3 by rotating the rotor 50.

  The rotor rotation mechanism 60 rotates the rotor 50 along the inner peripheral wall 12 of the housing 10 with the axis of the rotor 50 as the rotation center. FIG. 5 is a cross-sectional view taken along the line VV in FIG. In the present embodiment, the rotor rotation mechanism 60 includes a rotor support portion 61 and a motor 62. The rotor support portion 61 supports the rotor 50. In the present embodiment, the rotor support portion 61 described above supports a portion of the rotor 50 that faces the axial opening 53. The motor 62 rotates the rotor support portion 61 about the axis of the rotor 50 as the rotation center. Further, as described above, the rotor 50 is provided coaxially with the housing 10 and has a characteristic of spreading in the diameter increasing direction. Accordingly, the rotor 50 causes the outer peripheral surface of the rotor 50 to slide and rotate on the inner peripheral wall 12 of the housing 10 by the rotor rotating mechanism 60.

  Here, as shown in FIG. 5, in the inner peripheral wall 12 of the housing 10, the region where the first opening 70 and the second opening 80 do not face each other even when the rotor 50 rotates is at least the axis of the rotor 50. A plurality of groove portions 90 are formed over the length in the direction. As described above, in the control valve 1, the rotor rotating mechanism 60 slides and rotates the rotor 50 along the inner peripheral wall 12 of the housing 10, so that the central space 13 and the first communication hole 30 and the second communication hole 40 are connected. Switch the communication status. For this reason, the rotor 50 rotates only at a predetermined angle with respect to the axial center of the rotor 50. When the rotor 50 is slid and rotated along the inner peripheral wall 12 of the housing 10 at such a predetermined angle, the first opening 70 and the second opening 80 of the inner peripheral wall 12 of the housing 10 are not opposed at all. The portion corresponds to a region of the inner peripheral wall 12 of the housing 10 described above where the first opening 70 and the second opening 80 do not face each other even when the rotor 50 rotates. Such a region corresponds to a region denoted by reference symbol R in FIG.

  In such a region R, a plurality of groove portions 90 are formed in the circumferential direction from one end portion in the axial direction of the rotor 50 to the other end portion. Forming from one end in the axial direction of the rotor 50 to the other end means that the groove 90 is provided with a length equal to or longer than the axial length of the rotor 50.

  In the present embodiment, as shown in FIG. 5, the groove portion 90 has a triangular cross-sectional shape that is orthogonal to the axial direction of the rotor 50. In the region surrounded by the one-dot chain line in FIG. 5, an enlarged view of the state where the groove portion 90 and the rotor 50 overlap in the radial direction is shown. Here, when the two flat plates are slightly inclined from the parallel state and are arranged with a narrow gap, and the gap is filled with fluid, when the two flat plates move relative to each other, the fluid moves along with it. It is dragged into a narrow gap and the pressure in the gap increases. It is known that the friction force can be reduced by floating two flat plates together with this pressure. Such an effect is called a “wedge effect”. As described above, by making the cross-sectional shape of the groove portion 90 triangular, the rotor 50 and the inner peripheral wall 12 of the housing 10 can be brought into non-contact due to the wedge effect when the rotor 50 rotates. Therefore, sliding resistance can be reduced when the rotor 50 is rotated, and the rotor 50 can be easily rotated.

  Further, the groove 90 may be formed so that the cross-sectional area becomes narrower toward the downstream side in the flow direction of the fluid flowing along the inner peripheral wall 12 of the housing 10. The fluid flowing along the inner peripheral wall 12 of the housing 10 is a fluid introduced into the central space 13 through the first communication hole 30 and the second communication hole 40. FIG. 6 shows a cross-sectional view taken along line VI-VI in FIG. However, the rotor 50 is omitted. As shown in FIG. 1, in this embodiment, the fluid flows from the control valve 1 toward the pump 7. Therefore, the fluid introduced into the central space 13 circulates from bottom to top in FIG.

  Here, the pressure distribution in the wedge-shaped gap as shown in FIG. 7 is expressed by the equation (1).

ただし、Ｕはロータ５０の回転速度、Ｂは溝部９０の周方向に沿った幅の１／２、ｈはハウジング１０とロータ５０との距離、μは流体の粘度、Ｐは流体の圧力、Ｐ０はｘ＝０における圧力である。

Where U is the rotational speed of the rotor 50, B is half the width of the groove 90 along the circumferential direction, h is the distance between the housing 10 and the rotor 50, μ is the viscosity of the fluid, P is the pressure of the fluid, P0 Is the pressure at x = 0.

  As shown in the equation (1), the wider the groove 90, the higher the pressure, and the narrower the groove 90, the lower the pressure. Therefore, by gradually reducing the groove width of the groove portion 90 along the fluid flow direction, a fluid flow is formed in the groove portion 90 due to a pressure difference, and even if foreign matter is mixed in the fluid, It is possible to prevent clogging in the groove 90.

  Further, as shown in FIG. 6, since the groove portion 90 is formed in parallel with the axial center of the housing 10, the length until the groove portion 90 reaches from the one end portion in the axial direction of the rotor 50 to the other end portion is set. Can be as short as possible. Therefore, even when the foreign matter mixed in the fluid enters the groove portion 90, the foreign matter can be easily discharged from the groove portion 90.

  In the inner peripheral wall 12 of the housing 10, a seal surface 15 that is in liquid-tight contact with the rotor 50 is formed in a region where the first opening 70 and the second opening 80 face when the rotor 50 rotates. In the inner peripheral wall 12 of the housing 10, the region where the first opening 70 and the second opening 80 face each other when the rotor 50 rotates is a region denoted by reference sign S excluding the region R in FIG. 5. . The seal surface 15 is a surface that has been processed so that the outer peripheral surface of the rotor 50 is in close contact with the inner peripheral wall 12 of the housing 10. Since the inner peripheral wall 12 of the housing 10 is provided with the seal surface 15 over such a region S, the outer peripheral surface of the rotor 50 and the inner peripheral wall 12 of the housing 10 are formed in the first opening 70 and the second opening 80. It is possible to prevent fluid leakage (intrusion) between the two.

  Here, in the present embodiment, the control valve 1 is provided in the cooling circuit 100 of the vehicle. In such an application, the flow of the fluid is controlled by the control valve 1 to circulate the fluid to the engine 4 to cool the engine 4. However, the temperature of the control valve 1 rises due to the heat from the engine 4. On the other hand, when the temperature is high, the winding resistance of the coil of the motor increases and current cannot flow, so the output torque of the motor decreases. For this reason, since it is generally necessary to select a motor in consideration of output torque required at high temperatures, it is necessary to use a motor with a large rated output, which causes an increase in cost.

  Therefore, the rotor 50 according to the present embodiment is configured such that the spreading characteristics in the diameter expanding direction are reduced at high temperatures. As described above, the rotor 50 has a spreading characteristic in the diameter increasing direction and is configured to be in close contact with the inner peripheral wall 12 of the housing 10. When the rotor rotation mechanism 60 tries to rotate the rotor 50 but the rotor 50 stops rotating, the amount of heat from the engine 4 increases and the control valve 1 is warmed. The rotor 50 relaxes the spread in the diameter expansion direction by this heat. Such a characteristic can be realized by configuring the rotor 50 using a material having a characteristic of contracting at a higher temperature than at a low temperature. With this configuration, the spreading characteristics of the rotor 50 are reduced at high temperatures, so that the sliding resistance of the rotor 50 with respect to the inner peripheral wall 12 of the housing 10 can be reduced, and an inexpensive motor with a small rated output can be obtained. It can be used.

  Further, when the rotor 50 cannot rotate relative to the housing 10 for some reason, if at least one of the first communication hole 30 and the second communication hole 40 is in communication with the central space 13, the engine 4 is fluidized. Since the engine 4 can be cooled, the engine 4 may be overheated if both the first communication hole 30 and the second communication hole 40 are disconnected from the central space 13.

  Therefore, the rotor 50 is configured to be deformed from the inner peripheral wall 12 of the housing 10 to a separated state when the rotor 50 is in a temperature higher than a predetermined use temperature range. Thereby, when the rotor 50 is excessively warmed, the rotor 50 is reduced in diameter, and the pressing force of the rotor 50 against the inner peripheral wall 12 of the housing 10 becomes zero. In this case, fluid pressure acts on the rotor 50, and the rotor 50 is separated from the inner peripheral wall 12 of the housing 10. Therefore, regardless of the positions of the first opening 70 and the second opening 80, the first communication hole 30, the second communication hole 40, and the central space 13 can be brought into communication with each other. It becomes possible to circulate.

  Such a temperature characteristic of the rotor 50 is shown in FIG. The vertical axis of FIG. 8A shows the force F that the rotor 50 tries to spread outward in the radial direction, and the horizontal axis shows the temperature T of the rotor 50. As shown in FIG. 8A, if the temperature is lower than T1, the spreading characteristic of the rotor 50 does not change greatly. Therefore, as shown in FIG. 8B, the rotor 50 is rotated while being in close contact with the inner peripheral wall 12 of the housing 10. In FIGS. 8B to 8D, for easy understanding, the force F is indicated by an arrow, and the strength of the force F is indicated by the number of arrows. A broken arrow indicates the flow of fluid.

  If the temperature of the rotor 50 gradually increases (for example, if the temperature is equal to or higher than T1 and lower than T2), the force F of the rotor 50 becomes smaller than that when the temperature is lower than T1 as shown in FIG. 8C. (That is, the number of arrows is smaller than in FIG. 8B). For this reason, the adhesion between the rotor 50 and the inner peripheral wall 12 of the housing 10 is weaker than that when the temperature is less than T1, but the fluid does not leak between the rotor 50 and the housing 10. As a result, the torque of the motor 62 required to rotate the rotor 50 is reduced. Therefore, even if the temperature rises and the winding resistance increases, the current flowing through the winding resistance can be reduced, so that the rotor 50 can be appropriately rotated.

  Further, as shown in FIG. 8A, when the temperature of the rotor 50 increases (for example, when the temperature is equal to or higher than T2), the force F of the rotor 50 becomes smaller than when the temperature is lower than T2. In this case, as shown in FIG. 8 (d), the rotor 50 is reduced in diameter, and the rotor 50 is pressed by the fluid from the first communication hole 30 and the second communication hole 40, so that the inside of the rotor 50 and the housing 10. A gap is formed between the peripheral wall 12 and the peripheral wall 12. As indicated by the broken arrow, the fluid flows into this gap and circulates through the central space 13 via the first opening 70 and the second opening 80, so that the fluid can be circulated.

[Other Embodiments]
In the above-described embodiment, the rotor 50 is described as being configured so that the plate-like material is rounded into a cylindrical shape and the spreading property in the diameter-expanding direction is reduced at high temperatures. It is also possible to configure by bonding materials having different thermal expansion coefficients to the surface side. Specifically, materials having different thermal expansion coefficients can be stacked and configured like a bimetal. Such a structure can be configured by, for example, laminating two plate-like members having different thermal expansion coefficients and then rounding them into a cylindrical shape. Of course, it is also possible to configure by mounting one of two cylindrical members rounded in advance on the other outer peripheral surface or inner peripheral surface. According to such a rotor 50, when the material on the outer peripheral surface side expands in the circumferential direction at a high temperature, the material on the inner peripheral surface side receives a load in the diameter reducing direction, and promotes deformation of the rotor 50 at the high temperature. be able to. Therefore, since the sliding resistance of the rotor 50 with respect to the inner peripheral wall 12 of the housing 10 can be reduced, the rotor 50 can be easily rotated.

  Although the cross-sectional shape of the groove part 90 was demonstrated as the triangle in the said embodiment, it is also possible to comprise the cross-sectional shape of the groove part 90 with a tetragon | quadrangle or another polygon, and it is also possible to form it in a U shape. is there. Of course, other shapes can be used.

  In the above-described embodiment, the groove 90 is described as having a cross-sectional area that is narrower toward the downstream side in the flow direction of the fluid flowing along the inner peripheral wall 12 of the housing 10, but the groove 90 is formed on the inner peripheral wall 12 of the housing 10. The cross-sectional area can be made narrower toward the upstream side in the flow direction of the fluid flowing along, and the cross-sectional area can be formed uniformly regardless of the flow direction of the fluid.

  In the above-described embodiment, the groove portion 90 has been described as being formed in parallel with the axis of the housing 10, but the groove portion 90 may be formed in a spiral shape on the inner peripheral wall 12 of the housing 10.

  In the above embodiment, the rotor 50 is described as being configured to reduce the spread characteristic in the diameter expansion direction at high temperatures, but the rotor 50 does not change the spread characteristic in the diameter expansion direction regardless of the temperature. It is also possible to configure.

  In the above embodiment, the rotor 50 has been described as being configured to be deformed from the inner peripheral wall 12 of the housing 10 to a separated state when the rotor 50 is in a temperature higher than a predetermined use temperature range. However, the rotor 50 can be configured not to be separated from the inner peripheral wall 12 of the housing 10 even when the rotor 50 is hotter than the operating temperature range.

  In the above embodiment, the first communication hole 30 is provided on the top surface 11 side and the second communication hole 40 is provided on the bottom surface 14 side. However, the first communication hole 30 is on the bottom surface 14 side. The second communication hole 40 may be provided on the top surface 11 side.

  In the above embodiment, the control valve 1 brings the first communication hole 30 and the central space 13 into communication with each other through the first opening 70 and the second opening 80, and the second communication hole 40 and the central space 13. The state A in which the first communication hole 30 and the central space 13 are blocked, the state B in which the second communication hole 40 and the central space 13 are in communication, and the first communication hole 30 and the center. It has been described that the space 13 is in a blocked state and can be switched to either the state C in which the second communication hole 40 and the central space 13 are blocked. However, it is also possible to be configured to be switchable between two predetermined states. The three states, the first communication hole 30 and the central space 13 are in communication with each other, and the second communication hole 40 and the center are connected. It is also possible to configure so that it can be switched to four states including a state in which the space 13 is shut off.

  In the above embodiment, the control valve 1 has been described on the assumption that fluid flows in via the radiator 5 and the heater core 6. However, the control valve 1 is configured so that the fluid flows from the control valve 1 toward the radiator 5 and the heater core 6. Is also possible.

  The present invention can be used for a control valve for controlling fluid flow.

1: Control valve 7: Pump 10: Housing 12: Inner peripheral wall 13: Central space 15: Seal surface 20: Pump communication hole 30: First communication hole 40: Second communication hole 50: Rotor 60: Rotor rotation mechanism 70: First 1 opening 80: second opening 90: groove R: region

Claims (8)

A tubular housing;
A pump communication hole provided on one end surface in the axial direction of the housing and communicating with the pump;
A first communication hole provided in an inner peripheral wall of the housing;
A second communication hole provided in the inner peripheral wall at a position different from the first communication hole and the axial direction in the circumferential direction in the housing,
A cylindrical rotor that is accommodated coaxially with the housing in the housing and has a spreading characteristic in the diameter expanding direction;
A rotor rotation mechanism that rotates the rotor along the inner peripheral wall of the housing with the axis of the rotor as a rotation center;
A first opening that is formed in the rotor and switches a communication state between the first communication hole and a central space radially inward of the rotor according to the rotation of the rotor;
A second opening that is formed in the rotor and switches a communication state between the second communication hole and the central space according to the rotation of the rotor;
A plurality of grooves formed in the inner peripheral wall of the housing in a region where the first opening and the second opening do not face each other even when the rotor rotates, at least over the axial length of the rotor. When,
With control valve.   The control valve according to claim 1, wherein a cross-sectional shape of the groove portion is a triangle.   3. The control valve according to claim 1, wherein the groove has a cross-sectional area that is narrower toward the downstream side in the flow direction of the fluid flowing along the inner peripheral wall of the housing.   4. The control valve according to claim 1, wherein the groove is formed in parallel with an axis of the housing. 5.   A seal surface that is in liquid-tight contact with the rotor is formed in a region of the inner peripheral wall of the housing where the first opening and the second opening face when the rotor rotates. The control valve according to any one of 1 to 4.   The control valve according to any one of claims 1 to 5, wherein the rotor is configured to reduce spreading characteristics in the diameter-expanding direction at a high temperature.   The control valve according to claim 6, wherein the rotor is configured by bonding materials having different thermal expansion coefficients to the inner peripheral surface side and the outer peripheral surface side.   The control according to claim 6 or 7, wherein the rotor is configured to be deformed from the inner peripheral wall of the housing to a separated state when the rotor is in a temperature higher than a predetermined use temperature range. valve.

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