JP7142150B2 - control valve - Google Patents

Description

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a control valve used for, for example, switching flow paths of cooling water for vehicles.
This application claims priority based on Japanese Patent Application No. 2019-060919 filed on March 27, 2019, the content of which is incorporated herein.

In a cooling system that uses cooling water to cool the engine, in addition to the radiator flow path that circulates between the radiator and the engine, a bypass flow path that bypasses the radiator and a warm air flow path that passes through the oil warmer are installed. There is In this type of cooling system, a control valve is interposed at a branching portion of the flow path, and the flow path is appropriately switched by the control valve. A known control valve has a cylindrical valve element rotatably arranged in a casing, and opens and closes an arbitrary flow path in accordance with the rotational position of the valve element (see, for example, Patent Document 1). .

In the control valve disclosed in Patent Document 1, a casing is provided with an inlet into which a liquid such as cooling water flows and a plurality of outlets through which the liquid that has flowed in flows out to the outside. A plurality of valve holes communicating between the inside and the outside are formed in the peripheral wall of the valve body corresponding to the plurality of outflow ports. One end side of a substantially cylindrical seal tube member is slidably held in each outflow port. One end of each seal cylinder member communicates with the downstream side of the corresponding outflow port. Further, the other end portion of each seal cylinder member is provided with a valve sliding contact surface that slidably contacts the outer peripheral surface of the valve body. The valve sliding contact surface of each seal cylinder member is in sliding contact with the outer peripheral surface of the valve body at a position where it overlaps with the rotation path of the corresponding valve hole of the valve body.
The valve slide contact surface of the seal cylinder member is formed so as to follow the shape of the outer surface of the valve body so as to be in close contact with the outer peripheral surface of the valve body. That is, the other axial end portion of the tubular seal member has a protrusion height in the direction of the valve body that continuously changes in the circumferential direction of the tubular seal member so as to follow the shape of the outer surface of the valve body.

The valve body of the control valve allows the liquid to flow out from the inner region of the valve body to the corresponding outlet port when the tubular seal member is in a position where it communicates with the corresponding valve hole, and the tubular seal member communicates with the corresponding valve hole. When in a position out of communication with the hole, it blocks the outflow of liquid from the inner region of the valve body to the corresponding outlet. The rotational position of the valve body is controlled by an actuator such as an electric motor.

Japanese Patent Application Laid-Open No. 2017-3064

In the conventional control valve described above, the projection height of the other end of the cylindrical seal member changes continuously along the outer surface shape of the cylindrical valve body. Therefore, in the region of the other end of the cylindrical seal member where the protruding height is high, when the pressure of the liquid in the casing acts on the outer peripheral surface near the protruding end, the pressure pushes the other end of the cylindrical seal member. Acts as a moment for flexural deformation. Specifically, when the pressure of the liquid in the casing acts on the outer peripheral surface near the protruding end in the region of the other end of the sealing cylinder member where the protruding height is high, the force caused by the pressure acting on the outer peripheral surface acts as a moment originating from the low-protruding region of the other end of the cylindrical seal member, and flexurally deforms the low-protruding region of the cylindrical seal member away from the peripheral wall of the valve body. Therefore, when the pressure in the casing increases, there is a concern that the gap between the low-protrusion-height region of the cylindrical seal member and the peripheral wall portion of the valve body may increase.

The problem to be solved is to suppress the deformation of the tubular seal member due to the hydraulic pressure in the casing, and to improve the sealing performance between the tubular seal member and the valve body.

A control valve according to one embodiment of the present invention includes a casing having an inlet for inflow of liquid from the outside and an outlet for discharging the liquid that has flowed into the interior to the outside; one end in the axial direction communicates with the outflow port, and the other end in the axial direction of the valve body is provided with a rotation path of the valve hole. and a seal cylinder member provided with a valve sliding contact surface that slidably contacts the outer peripheral surface of the peripheral wall portion at a position where at least a part overlaps with, the other axial end of the seal cylinder member , in a control valve in which a height of protrusion in a direction toward said peripheral wall portion continuously changes in a circumferential direction along a shape of an outer peripheral surface of said peripheral wall portion, the outer peripheral surface of said peripheral wall of said other end portion of said cylindrical seal member; A small outer diameter portion having a shorter length from the axial center of the seal cylinder member to the outer peripheral surface than other regions is provided in a region having a high protrusion height, and the small outer diameter portion is The end portion on the side of the valve sliding contact surface is constituted by a first plane having a linear shape substantially parallel to the rotation axis of the valve body, and the projection height of the peripheral wall of the other end portion of the cylindrical seal member A second plane substantially parallel to the first plane is formed on the inner peripheral surface of the high region so as to bulge inward in the radial direction of the tubular seal member .

With the above configuration, when the other axial end portion of the cylindrical seal member is closed by the outer peripheral surface of the peripheral wall portion of the valve body, the outflow of liquid from the inside of the valve body to the outflow port is blocked. When the valve body rotates from this state and the other axial end of the sealing tube member communicates (wraps) with the valve hole of the valve body, the liquid flows out from the inside of the valve body to the outflow port. When the other axial end portion of the tubular seal member is closed by the outer peripheral surface of the peripheral wall portion of the valve body, the valve sliding contact surface of the tubular seal member is pressed against the peripheral wall portion of the valve body. At this time, the pressure of the liquid in the casing acts on the outer circumference of the other end of the cylindrical seal member. In the region of the other end of the cylindrical seal member where the protruding height is high, force due to the pressure of the liquid in the casing acts on the outer peripheral surface near the protruding end. This force acts on the other end portion side of the tubular seal member as a moment originating from the area where the protrusion height is low. However, in the control valve according to the present invention, since the small outer diameter portion is provided in the region of the other end portion of the seal cylinder member where the projection height is high, the pressure receiving surface of the region where the projection height is high (small outer diameter diameter) to the starting point of the moment becomes shorter. As a result, the moment acting on the other end portion of the tubular seal member is reduced, and the flexural deformation of the other end portion of the tubular seal member due to the moment is suppressed.

In this case, when the area of the other end portion of the cylindrical seal member with a high projection height receives the hydraulic pressure in the casing, the end portion of the linear small outer diameter portion comes into line contact with the peripheral wall portion of the valve body. It will be. For this reason, the contact range with the outer surface of the valve body is wider than when the arc-shaped outer surface makes point contact with the peripheral wall portion of the valve body. As a result, the wear of the other end of the tubular seal member is further suppressed.

In this case, since the radial width (thickness) of the high protruding height region of the other end of the seal cylinder member can be kept substantially constant, the decrease in the radial width of the valve sliding contact surface increases the surface pressure. can be suppressed. As a result, it becomes possible to further suppress wear of the other end of the seal cylinder member.

The seal cylinder member is positioned on the one end side and communicates with the outflow port, and is positioned on the other end side, and the axial end face constitutes the valve sliding contact surface, and a second cylindrical portion formed by swelling the second plane on an inner peripheral surface, wherein the inner diameter of the first cylindrical portion is formed smaller than the inner diameter of the second cylindrical portion. Also good.

In this case, the flow rate of the liquid that flows downstream of the outflow port through the tubular seal member is determined by the inner diameter of the first tubular portion of the tubular seal member, which has a relatively small inner diameter. The second flat surface formed by bulging to the inner peripheral side is provided radially inward of the second cylindrical portion having a relatively large inner diameter, and thus has an effect on the flow rate of the liquid flowing out downstream of the outlet. do not give Therefore, when this configuration is adopted, it is possible to easily set and adjust the flow rate of the liquid flowing out of the outlet.

A control valve according to another aspect of the present invention comprises a casing having an inlet for inflow of liquid from the outside and an outlet for discharging the liquid that has flowed into the interior to the outside, and rotatably arranged inside the casing, A valve body having a peripheral wall portion formed with a valve hole communicating between the inside and the outside, one axial end communicating with the outflow port, and the other axial end having a rotation of the valve hole of the valve body. a seal cylinder member provided with a valve sliding contact surface that slidably abuts against the outer peripheral surface of the peripheral wall portion at a position where at least a part overlaps with the path, the other axial end portion of the seal cylinder member is a control valve in which the protrusion height in the direction toward the peripheral wall portion changes continuously in the circumferential direction along the shape of the outer peripheral surface of the peripheral wall portion; A small outer diameter portion whose length from the axial center of the seal cylinder member to the outer peripheral surface is shorter than that of other regions is provided in a region of the surface where the projection height is high, and the seal cylinder member has the above-described The outer peripheral surface of the peripheral wall of the other end is characterized by being formed in a substantially elliptical shape in which the region with the highest protruding height is the minor axis and the region with the lowest protruding height is the major axis.

In this case, since the outer peripheral surface of the other end of the tubular seal member smoothly changes into a substantially elliptical shape, the other end of the tubular seal member is less likely to cause unnecessary turbulence in the flow inside the casing.

The radial width of the other end portion of the tubular seal member may be formed to have a constant width in the peripheral area of the tubular seal member.

In this case, it is possible to suppress an increase in surface pressure due to a partial reduction in the radial width of the valve sliding contact surface. As a result, it becomes possible to further suppress wear of the other end of the seal cylinder member.

The seal cylinder member includes a first cylinder part located on the one end side and communicating with the outflow port, and a second cylinder part located on the other end side and having an axial end surface forming the valve sliding contact surface. and a tubular portion, wherein the outer peripheral surface and the inner peripheral surface of the peripheral wall of the second tubular portion are substantially elliptical, with the region having the highest protrusion height being the minor axis and the region having the lowest protrusion height being the major diameter. The inner peripheral surface of the region of the second tubular portion having the highest protrusion height may be formed continuously with the inner peripheral surface of the first tubular portion without a step.

In this case, since there is no stepped portion that serves as a bending starting point between the inner peripheral surface of the region with the highest protrusion height of the second tubular portion and the inner peripheral surface of the first tubular portion, the protrusion height of the second tubular portion Even if the hydraulic pressure in the casing acts on the outer peripheral surface near the protruding end of the highest region of the pressure, bending deformation is less likely to occur between the first tubular portion and the second tubular portion.

The radial width of the low protruding height region of the other end may be formed wider than the radial width of the high protruding height region of the other end.

In this case, of the other end portion of the seal cylinder member, since the width in the radial direction of the low protruding height region where the Hertzian surface pressure tends to increase is formed to be wide, the surface pressure at the low protruding height portion increase can be suppressed. Therefore, it is possible to suppress premature wear of the portion of the other end portion of the seal cylinder member having a low projection height.

In the above-described control valve, the length from the axial center of the seal cylinder member to the outer peripheral surface of the seal cylinder member is longer than other areas in the area of the outer peripheral surface of the peripheral wall of the other end portion of the seal cylinder member where the protrusion height is high. Since the small outer diameter portion is provided, it is possible to suppress the generation of a moment due to the hydraulic pressure received by the outer peripheral surface of the region with a high protrusion height, and to suppress the bending deformation of the other end portion of the seal cylinder member. can be done. Therefore, when the above-described control valve is adopted, it is possible to improve the sealing performance between the seal cylinder member and the valve body.

1 is a block diagram of a cooling system according to an embodiment; FIG. 1 is a perspective view of a control valve according to a first embodiment; FIG. 1 is an exploded perspective view of a control valve according to a first embodiment; FIG. 3 is a cross-sectional view taken along line IV-IV of FIG. 2; FIG. 3 is an enlarged view along line VV of FIG. 2; FIG. 6 is an enlarged view of the VI part of FIG. 5; FIG. It is a perspective view of a seal cylinder member of a 1st embodiment. It is an end view of the seal cylinder member of 1st Embodiment. It is a perspective view of the seal cylinder member of 2nd Embodiment. It is an end view of the seal cylinder member of 2nd Embodiment. FIG. 11 is a cross-sectional view along line XI-XI of FIG. 10 of the seal cylinder member of the second embodiment; FIG. 11 is a cross-sectional view along the XII-XII line in FIG. 10 of the seal cylinder member of the second embodiment; It is a perspective view of the seal cylinder member of 3rd Embodiment. It is an end view of the seal cylinder member of 3rd Embodiment.

BEST MODE FOR CARRYING OUT THE INVENTION Hereinafter, embodiments of the present invention will be described with reference to the drawings. In the following description, a case in which the control valve of this embodiment is employed in a cooling system that cools the engine using cooling water will be described. In addition, in each embodiment, the same parts are denoted by common reference numerals, and overlapping descriptions are omitted.

<Cooling system>
FIG. 1 is a block diagram of a cooling system 1. FIG.
As shown in FIG. 1, the cooling system 1 is mounted on a vehicle having at least an engine as a vehicle drive source. The vehicle may be a hybrid vehicle, a plug-in hybrid vehicle, or the like, in addition to a vehicle having only an engine.

The cooling system 1 includes an engine 2 (ENG), a water pump 3 (W/P), a radiator 4 (RAD), a heat exchanger 5 (H/EX), a heater core 6 (HTR), an EGR cooler 7 (EGR) and a control A valve 8 (EWV) is connected by various flow paths 10-14.
The water pump 3 , the engine 2 and the control valve 8 are connected in order from upstream to downstream on the main flow path 10 . In the main flow path 10 , the cooling water (liquid) passes through the engine 2 and the control valve 8 in order due to the operation of the water pump 3 .

A radiator channel 11, a warm-up channel 12, an air conditioning channel 13, and an EGR channel 14 are connected to the main channel 10, respectively. The radiator flow path 11 , warm-up flow path 12 , air conditioning flow path 13 and EGR flow path 14 connect the upstream portion of the water pump 3 and the control valve 8 in the main flow path 10 .

A radiator 4 is connected to the radiator flow path 11 . In the radiator passage 11 , heat exchange is performed between the cooling water and the outside air in the radiator 4 .

A heat exchanger 5 is connected to the warm-up flow path 12 . Engine oil circulates through an oil flow path 18 between the heat exchanger 5 and the engine 2 . In the warm-up flow path 12 , heat exchange is performed between the cooling water and the engine oil in the heat exchanger 5 . That is, the heat exchanger 5 functions as an oil warmer to heat the engine oil when the water temperature is higher than the oil temperature. On the other hand, the heat exchanger 5 functions as an oil cooler to cool the engine oil when the water temperature is lower than the oil temperature.

A heater core 6 is connected to the air conditioning flow path 13 . The heater core 6 is provided, for example, in a duct (not shown) of an air conditioner. In the air-conditioning flow path 13, the heater core 6 exchanges heat between the cooling water and the air-conditioned air flowing through the duct.

An EGR cooler 7 is connected to the EGR flow path 14 . In the EGR flow path 14 , heat exchange between cooling water and EGR gas takes place in the EGR cooler 7 .

In the cooling system 1 described above, the cooling water that has passed through the engine 2 in the main passage 10 flows into the control valve 8 and is then selectively distributed to the various passages 11 to 13 by the operation of the control valve 8 . As a result, early temperature rise and high water temperature (optimal temperature) control can be realized, and the fuel efficiency of the vehicle is improved.

<Control valve>
FIG. 2 is a perspective view of the control valve 8 of the first embodiment. 3 is an exploded perspective view of the control valve 8. FIG.
As shown in FIGS. 2 and 3, the control valve 8 mainly includes a casing 21, a valve body 22 (see FIG. 3), and a drive unit .

<Casing>
The casing 21 has a cylindrical casing body 25 with a bottom and a lid 26 that closes the opening of the casing body 25 . In the following description, the direction along the axis O1 of the casing 21 is simply referred to as the case axial direction. In the case axial direction, the direction toward the bottom wall portion 32 of the casing body 25 with respect to the case peripheral wall 31 of the casing body 25 is called the first side, and the direction toward the lid body 26 with respect to the case peripheral wall 31 of the casing body 25 is called the first side. called the second side. Further, the direction perpendicular to the axis O1 is called the case radial direction, and the direction around the axis O1 is called the case circumferential direction.

A plurality of mounting pieces 33 are formed on the case peripheral wall 31 of the casing main body 25 . Each mounting piece 33 protrudes outward in the case radial direction from the case peripheral wall 31 . The control valve 8 is fixed in the engine room via each mounting piece 33, for example. The position, number, etc. of each mounting piece 33 can be changed as appropriate.

FIG. 4 is a cross-sectional view taken along line IV-IV of FIG.
As shown in FIGS. 3 and 4, a portion of the case peripheral wall 31 located on the second side is formed with an inflow port 37 that bulges outward in the case radial direction. The inflow port 37 is formed with an inflow port 37a (see FIG. 4) penetrating the inflow port 37 in the radial direction of the case. The inflow port 37 a communicates the inside and outside of the casing 21 . The opening end face of the inflow port 37 (the outer end face in the radial direction of the case) is connected to the above-described main flow path 10 (see FIG. 1).

As shown in FIG. 4, in the case peripheral wall 31, a radiator port 41 that bulges outward in the case radial direction is formed at a position facing the inflow port 37 in the case radial direction with the axis O1 interposed therebetween. . The radiator port 41 is formed with a fail opening 41a and a radiator outlet 41b (outlet) arranged side by side in the axial direction of the case. The fail opening 41a and the radiator outlet 41b penetrate the radiator port 41 in the radial direction of the case. In this embodiment, the fail opening 41a faces the inlet 37a described above in the radial direction of the case. The radiator outlet 41b is located on the first side in the axial direction of the case with respect to the fail opening 41a.

A radiator joint 42 is connected to the opening end face of the radiator port 41 (the outer end face in the radial direction of the case). The radiator joint 42 connects between the radiator port 41 and the upstream end of the radiator flow path 11 (see FIG. 1). The radiator joint 42 is welded (for example, by vibration welding) to the opening end face of the radiator port 41 .

A thermostat 45 is provided in the fail opening 41a. The thermostat 45 faces the inlet 37a described above in the radial direction of the case. The thermostat 45 opens and closes the fail opening 41 a according to the temperature of the cooling water flowing inside the casing 21 .

An EGR outflow port 51 is formed in a portion of the lid body 26 that is positioned closer to the radiator port 41 in the case radial direction with respect to the axis O1. The EGR outlet 51 penetrates the lid 26 in the axial direction of the case. In this embodiment, the EGR outlet 51 intersects (perpendicularly) with the opening direction (case radial direction) of the fail opening 41a. At least a portion of the EGR outlet 51 overlaps the thermostat 45 in a front view seen from the case axial direction.

An EGR joint 52 is formed at the opening edge of the EGR outlet 51 in the lid 26 . The EGR joint 52 is formed in a tubular shape extending outward in the radial direction of the case toward the second side in the axial direction of the case, and is between the EGR outlet 51 and the upstream end of the EGR flow path 14 (see FIG. 1). are connected.

As shown in FIG. 3 , a warm-up port 56 that bulges outward in the case radial direction is formed in a portion of the case peripheral wall 31 positioned closer to the first side in the case axial direction than the radiator port 41 . The warm-up port 56 is formed with a warm-up outlet 56a (outlet) that penetrates the warm-up port 56 in the radial direction of the case. A warm-up joint 62 is connected to the opening end face of the warm-up port 56 . A warm-up joint 62 connects the warm-up port 56 and the upstream end of the warm-up flow path 12 (see FIG. 1) described above. The warm-up joint 62 is welded (for example, by vibration welding or the like) to the open end surface of the warm-up port 56 .

As shown in FIGS. 2 and 3, in the case peripheral wall 31, between the radiator port 41 and the warm-up port 56 in the case axial direction, and about 180° in the case peripheral direction with respect to the warm-up port 56 An air conditioning port 66 is formed at the shifted position. The air-conditioning port 66 is formed with an air-conditioning outlet 66a (outlet) penetrating the air-conditioning port 66 in the radial direction of the case. An air conditioning joint 68 is connected to the opening end face of the air conditioning port 66 . The air conditioning joint 68 connects the air conditioning port 66 with the upstream end of the air conditioning flow path 13 (see FIG. 1). The air-conditioning joint 68 is welded (for example, by vibration welding) to the open end surface of the air-conditioning port 66 .

<Drive unit>
As shown in FIG. 2 , the drive unit 23 is attached to the bottom wall portion 32 of the casing body 25 . The drive unit 23 includes a motor, a speed reduction mechanism, a control board, etc. (not shown) housed in a unit case.

<Rotor>
As shown in FIGS. 3 and 4, the valve body 22 is housed inside the casing 21 . The valve body 22 is formed in a cylindrical shape and arranged coaxially with the axis O1 of the casing 21 inside the casing 21 . The valve body 22 rotates around the axis O1 to open and close the above-described outflow ports (radiator outflow port 41b, warm-up outflow port 56a, and air conditioning outflow port 66a).

As shown in FIG. 4 , the valve body 22 is constructed by insert-molding an inner shaft portion 73 inside a rotor body 72 . The inner shaft portion 73 extends coaxially with the axis O1.

A first side end portion of the inner shaft portion 73 penetrates the bottom wall portion 32 in the axial direction of the case through a through hole (atmospheric release portion) 32a formed in the bottom wall portion 32 . A first side end portion of the inner shaft portion 73 is rotatably supported by a first bush (first bearing) 78 provided on the bottom wall portion 32 described above. Specifically, the bottom wall portion 32 is formed with a first shaft housing wall 79 toward the second side in the axial direction of the case. The first shaft housing wall 79 surrounds the through hole 32a described above. The above-described first bushing 78 is fitted inside the first shaft housing wall 79 .

A connecting portion 73a is formed in a portion of the inner shaft portion 73 located on the first side in the axial direction of the case relative to the first bushing 78 (a portion located outside the bottom wall portion 32). The connecting portion 73 a is connected to the drive unit 23 described above outside the casing 21 . Thereby, the power of the drive unit 23 is transmitted to the inner shaft portion 73 .

A second side end portion of the inner shaft portion 73 is rotatably supported by a second bush (second bearing) 84 provided on the lid body 26 described above. Specifically, a second shaft housing wall 86 is formed in the lid body 26 toward the first side in the axial direction of the case. The second shaft housing wall 86 surrounds the axis O1 inside the EGR outlet 51 in the radial direction of the case. The above-described second bushing 84 is fitted inside the second shaft housing wall 86 .

The rotor body 72 surrounds the inner shaft portion 73 described above. The rotor body 72 has an outer shaft portion 81 that covers the inner shaft portion 73 , a peripheral wall portion 82 that surrounds the outer shaft portion 81 , and spoke portions 83 that connect the outer shaft portion 81 and the peripheral wall portion 82 . .

The outer shaft portion 81 surrounds the entire circumference of the inner shaft portion 73 with both ends of the inner shaft portion 73 in the case axial direction exposed. In this embodiment, the outer shaft portion 81 and the inner shaft portion 73 constitute a rotating shaft 85 of the valve body 22 .

A first lip seal 87 is provided in a portion located on the second side in the case axial direction with respect to the first bushing 78 in the first shaft housing wall 79 described above. The first lip seal 87 seals between the inner peripheral surface of the first shaft housing wall 79 and the outer peripheral surface of the rotating shaft 85 (outer shaft portion 81). A portion of the first shaft housing wall 79 positioned closer to the first side in the case axial direction than the first lip seal 87 is open to the atmosphere through the through hole 32a.

On the other hand, a second lip seal 88 is provided in a portion located on the first side in the axial direction of the case with respect to the second bushing 84 inside the second shaft housing wall 86 described above. The second lip seal 88 seals between the inner peripheral surface of the second shaft housing wall 86 and the outer peripheral surface of the rotary shaft 85 (outer shaft portion 81). The cover 26 is formed with a through hole (atmospheric release portion) 98 penetrating through the cover 26 in the axial direction of the case.

A peripheral wall portion 82 of the valve body 22 is arranged coaxially with the axis O1. The peripheral wall portion 82 is arranged in a portion of the casing 21 located on the first side in the axial direction of the case relative to the inlet 37a. Specifically, the peripheral wall portion 82 is arranged at a position that avoids the fail opening 41a and straddles the radiator outlet 41b, the warm-up outlet 56a, and the air conditioning outlet 66a in the axial direction of the case. The inner side of the peripheral wall portion 82 constitutes a flow passage 91 through which the cooling water that has flowed into the casing 21 through the inlet 37a flows in the axial direction of the case. On the other hand, in the casing 21 , a portion located on the second side in the axial direction of the case with respect to the peripheral wall portion 82 constitutes a connection flow path 92 that communicates with the flow path 91 . Between the outer peripheral surface of the peripheral wall portion 82 and the inner peripheral surface of the case peripheral wall 31, a gap C2 is provided in the case radial direction.

A valve hole 95 penetrating the peripheral wall portion 82 in the radial direction of the case is formed in the peripheral wall portion 82 at the same position in the case axial direction as the radiator outlet 41b. When the valve hole 95 is at least partially overlapped with the seal cylinder member 131 inserted into the radiator outlet 41b as viewed from the radial direction of the case, the inside of the peripheral wall portion 82 (the flow passage 91) and the radiator outlet 41b through the valve hole 95 are formed. communicate with.

In the peripheral wall portion 82, another valve hole 96 is formed through the peripheral wall portion 82 in the case radial direction at the same position in the case axial direction as the warm-up outlet 56a. When the valve hole 96 at least partially overlaps with the seal cylindrical member 131 inserted into the warm-up outlet 56a as seen from the radial direction of the case, the warm-up flow flows through the peripheral wall portion 82 (circulation passage 91) through the valve hole 96. It communicates with the outlet 56a.

In the peripheral wall portion 82, another valve hole 97 is formed at the same position in the case axial direction as the air conditioning outlet 66a described above, and penetrates the peripheral wall portion 82 in the case radial direction. When the valve hole 97 overlaps at least a portion of the cylindrical seal member 131 inserted into the air conditioning outlet 66a as viewed from the radial direction of the case, the inside of the peripheral wall portion 82 (the flow passage 91) and the air conditioning outlet 66a through the valve hole 97 are arranged. communicate with.

As the valve element 22 rotates about the axis O1, it switches between communication and blocking between the valve holes 95, 96, 97 and the outflow ports 41b, 56a, 66a corresponding thereto. The pattern of communication between the valve holes 95, 96, 97 and the outlets 41b, 56a, 66a can be appropriately set.

Next, the details of the connection between the warm-up port 56 and the warm-up joint 62 will be described. The connecting portion between the radiator port 41 and the radiator joint 42 and the connecting portion between the air-conditioning port 66 and the air-conditioning joint 68 have the same configuration as the connecting portion between the warm-up port 56 and the warm-up joint 62. omitted.

FIG. 5 is an enlarged cross-sectional view corresponding to line VV in FIG. In the following description, the direction along the axis O2 of the warm-up outlet 56a may be referred to as the port axial direction (first direction). In this case, in the port axial direction, the direction toward the axis O1 with respect to the warm-up port 56 is called the inside, and the direction away from the axis O1 with respect to the warm-up port 56 is called the outside. Further, the direction perpendicular to the axis O2 may be referred to as the port radial direction (second direction), and the direction around the axis O2 may be referred to as the port circumferential direction.
As shown in FIG. 5, the warm-up port 56 has a tubular seal portion 101 extending in the axial direction of the port, and a port flange portion 102 projecting outward from the tubular seal portion 101 in the port radial direction. The inner side of the seal tube portion 101 constitutes the warm-up outlet 56a (outlet) described above. In this embodiment, the inner diameter of the seal cylinder portion 101 is set uniformly in the region except for the outer end portion in the port axial direction.

A surrounding wall 105 projecting outward in the port axial direction is formed on the outer peripheral portion of the port flange portion 102 . The surrounding wall 105 is formed all around the port flange portion 102 . A port joint portion 106 projecting outward in the port axial direction is formed in a portion of the port flange portion 102 located inside the surrounding wall 105 in the port radial direction. The port joint portion 106 is formed over the entire circumference of the port flange portion 102 .

The warm-up joint 62 has a joint tubular portion 110 arranged coaxially with the axis O2, and a joint flange portion 111 projecting outward in the port radial direction from the inner end portion of the joint tubular portion 110 in the port axial direction. ing.

The joint flange portion 111 is formed in an annular shape with an outer diameter equal to that of the port flange portion 102 and an inner diameter larger than the outer diameter of the seal tubular portion 101 . A joint connection portion 113 is formed on the inner peripheral portion of the joint flange portion 111 so as to protrude inward in the port axial direction. The joint joint 113 faces the port joint 106 in the port axial direction. The warm-up port 56 and the warm-up joint 62 are joined to each other by vibration welding the facing surfaces of the port joint portion 106 and the joint joint portion 113 .

The joint tubular portion 110 extends outward in the port axial direction from the inner peripheral edge of the joint flange portion 111 . The joint tubular portion 110 is formed in a multistage tubular shape whose diameter gradually decreases toward the outside in the port axial direction. Specifically, the joint tubular portion 110 has a large-diameter portion 121, a medium-diameter portion 122, and a small-diameter portion 123 successively extending outward in the port axial direction.

The large-diameter portion 121 surrounds the tubular seal portion 101 while being spaced outward in the port radial direction from the tubular seal portion 101 described above. The medium-diameter portion 122 faces the cylindrical seal portion 101 with a gap Q1 in the port axial direction.

A seal mechanism 130 is provided in a portion surrounded by the warm-up port 56 and the warm-up joint 62 . The seal mechanism 130 has a seal tubular member 131 , a biasing member 132 , a seal ring 133 and a holder 134 . As shown in FIG. 3, a seal mechanism 130 having the same structure as the seal mechanism 130 provided in the warm-up port 56 is also provided in the radiator port 41 and the air conditioning port 66 described above. In the description of the present embodiment, the seal mechanisms 130 provided in the radiator port 41 and the air conditioning port 66 are denoted by the same reference numerals as those of the seal mechanisms 130 provided in the warm-up port 56, and description thereof is omitted. .

As shown in FIG. 5, the seal cylinder member 131 is inserted into the warm-up outlet 56a. The seal cylinder member 131 has a peripheral wall extending coaxially with the axis O2. The peripheral wall of the seal cylinder member 131 is formed in a multi-stage tubular shape whose outer diameter gradually decreases toward the outside in the port axial direction. Specifically, the peripheral wall of the seal tubular member 131 includes a first tubular portion 142 located outside in the port axial direction (one end side in the axial direction) and communicating with the downstream side of the warm-up outlet 56a, and and a second cylindrical portion 141 positioned inside (the other end side in the axial direction) of and having an inner diameter and an outer diameter larger than those of the first cylindrical portion 142 .

The cylindrical seal member 131 has a large-diameter second cylindrical portion 141 slidably inserted into the inner peripheral surface of the cylindrical seal portion 101 . The inner end surface of the second cylindrical portion 141 in the port axial direction constitutes a valve sliding contact surface 141 a that slidably contacts the outer peripheral surface of the peripheral wall portion 82 of the valve body 22 . In this embodiment, the valve sliding contact surface 141a is a curved surface formed along the radius of curvature of the outer peripheral surface of the peripheral wall portion 82. As shown in FIG.

The outer peripheral surface of the first cylindrical portion 142 is continuous with the outer peripheral surface of the second cylindrical portion 141 via a stepped surface 143 . The step surface 143 inclines outward in the port radial direction as it goes inward in the port axial direction, and then extends further outward in the port radial direction. Therefore, between the outer peripheral surface of the small-diameter first cylindrical portion 142 and the inner peripheral surface of the sealing cylindrical portion 101, a seal gap Q2 is provided in the port radial direction.

An outer end surface of the first cylindrical portion 142 in the port axial direction (hereinafter referred to as "seat surface 142a") is a flat surface orthogonal to the port axial direction. The seat surface 142a of the first tubular portion 142 is arranged at the same position as the outer end surface of the tubular seal portion 101 in the port axial direction. The seal cylinder member 131 is separated from the warm-up joint 62 in the port radial direction and the port axial direction.

The biasing member 132 is interposed between the seat surface 142 a of the seal cylinder member 131 and the inner end surface of the small diameter portion 123 of the warm-up joint 62 in the port axial direction. The biasing member 132 is, for example, a wave spring. The biasing member 132 biases the seal cylinder member 131 inward in the port axial direction (toward the peripheral wall portion 82).

The seal ring 133 is, for example, Y packing. The seal ring 133 is externally fitted on the first tubular portion 142 of the tubular seal member 131 with the opening (forked portion) directed inward in the port axial direction. Specifically, while the seal ring 133 is arranged in the above-described seal gap Q2, each tip of the bifurcated portion slides on the outer peripheral surface of the first cylindrical portion 142 and the inner peripheral surface of the seal cylindrical portion 101, respectively. as close as possible. In the seal gap Q2, the area inside the seal ring 133 in the port axial direction cools the inside of the casing 21 through the gap between the inner peripheral surface of the seal cylinder portion 101 and the second cylinder portion 141 of the seal cylinder member 131. Hydraulic pressure of water is introduced. The step surface 143 is formed in a direction opposite to the valve sliding contact surface 141a of the seal cylinder member 131 in the port axial direction. The step surface 143 constitutes a pressure receiving surface that receives the hydraulic pressure of the cooling water in the casing 21 and is pressed inward in the port axial direction.

FIG. 6 is an enlarged view of the VI part of FIG.
Here, in the seal cylinder member 131, the area S1 of the stepped surface 143 and the area S2 of the valve sliding contact surface 141a are set so as to satisfy the following expressions (1) and (2).
S1<S2≦S1/k (1)
α≦k<1 (2)
k: pressure reduction constant of the cooling water flowing through the minute gap between the valve sliding contact surface 141a and the peripheral wall portion 82 of the valve body 22 α: lower limit value of the pressure reduction constant determined by the physical properties of the cooling water Note that the area of the stepped surface 143 The area S2 of S1 and the valve sliding contact surface 141a means the area when projected in the port axial direction.

α in equation (2) is a standard value of the pressure reduction constant determined by the type of cooling water, the usage environment (for example, temperature), and the like. For example, under normal use conditions, α=1/2 for water. When the physical properties of the cooling water used change, α changes to 1/3 or the like.
The pressure reduction constant k in equation (2) is a standard value of the pressure reduction constant when the valve sliding contact surface 141a is in uniform contact with the peripheral wall portion 82 from the outer edge to the inner edge in the port radial direction. α (eg, 1/2). However, the gap between the outer peripheral portion of the valve sliding contact surface 141a and the peripheral wall portion 82 slightly increases with respect to the inner peripheral portion of the valve sliding contact surface 141a due to manufacturing errors, assembly errors, etc. of the seal cylinder member 131. Sometimes. In this case, the pressure reduction constant k in equation (2) gradually approaches k=1.

In this embodiment, it is assumed that there is a minute gap between the valve sliding contact surface 141a of the seal cylinder member 131 and the outer peripheral surface of the peripheral wall portion 82 to allow sliding. The relationship between the areas S1 and S2 of the contact surface 141a is determined by equations (1) and (2).
That is, the pressure of the cooling water in the casing 21 directly acts on the step surface 143 of the seal cylinder member 131 as described above. On the other hand, the pressure of the cooling water in the casing 21 does not act on the valve sliding contact surface 141a. Specifically, the pressure of the cooling water decreases when the cooling water flows through the small gap between the valve sliding contact surface 141a and the peripheral wall portion 82 from the outer edge toward the inner edge in the port radial direction. It works together. At this time, the pressure of the cooling water tends to push up the seal cylinder member 131 outward in the port axial direction while gradually decreasing inward in the port radial direction.

As a result, a force obtained by multiplying the area S1 of the stepped surface 143 by the pressure P inside the casing 21 acts on the stepped surface 143 of the cylindrical seal member 131 as it is. On the other hand, a force obtained by multiplying the area S2 of the valve sliding contact surface 141a by the pressure P in the casing 21 and the pressure reduction constant k acts on the valve sliding contact surface 141a of the seal cylinder member 131 .

The areas S1 and S2 of the control valve 8 of the present embodiment are set so that k×S2≦S1 holds, as is clear from the equation (1). Therefore, the relationship P×k×S2≦P×S1 is also established.
Therefore, the force F1 (F1=P×S1) in the pressing direction acting on the stepped surface 143 of the tubular seal member 131 is the force F2 (F2=P× k×S2) or more. Therefore, in the control valve 8 of the present embodiment, it is possible to seal between the cylindrical seal member 131 and the peripheral wall portion 82 only by the pressure relationship of the cooling water in the casing 21 .

On the other hand, in this embodiment, as described above, the area S1 of the stepped surface 143 of the tubular seal member 131 is smaller than the area S2 of the valve sliding contact surface 141a. Therefore, even if the pressure of the cooling water in the casing 21 increases, it is possible to prevent the valve sliding contact surface 141a of the seal cylinder member 131 from being pressed against the peripheral wall portion 82 with an excessive force. Therefore, when the control valve 8 of the present embodiment is employed, it is possible to avoid an increase in the size and output of the drive unit 23 that rotationally drives the valve body 22, and furthermore, the seal cylindrical member 131, the bushes 78, and the like can be avoided. Premature wear of 84 (see FIG. 4) can be suppressed.

As described above, in the present embodiment, the pressure force acting on the tubular seal member 131 toward the inside in the port axial direction does not fall below the lifting force acting on the tubular seal member 131 toward the outside in the port axial direction. The area S2 of the sliding contact surface 141a is set larger than the area S1 of the stepped surface 143a. Therefore, it is possible to seal between the tubular seal member 131 and the peripheral wall portion 82 while suppressing the pressing of the tubular seal member 131 against the peripheral wall portion 82 with an excessive force.

The holder 134 described above is configured to be movable in the port axial direction with respect to the warm-up port 56 and the warm-up joint 62 within the gap Q1. Moreover, the holder 134 is arranged in at least one of the warm-up port 56 and the warm-up joint 62 so as to be separated in the port axial direction. The holder 134 has a holder tubular portion 151 , a holder flange portion 152 and a restricting portion 153 .

The holder tubular portion 151 extends in the port axial direction. The holder cylindrical portion 151 is inserted into the seal gap Q2 from the outside in the port axial direction. The bottom portion of the seal ring 133 described above can come into contact with the inner end surface of the holder cylindrical portion 151 in the port axial direction. That is, the holder tubular portion 151 restricts the outward movement of the seal ring 133 in the port axial direction.

The holder flange portion 152 protrudes outward in the port radial direction from the outer end portion of the holder cylindrical portion 151 in the port axial direction. The holder flange portion 152 is disposed in a gap Q1 between the axially outer end surface of the seal cylinder portion 101 and the inner end surface of the intermediate diameter portion 122 in the port axial direction. The inward movement of the holder 134 in the port axial direction is restricted by the seal tube portion 101 , and the outward movement of the holder 134 in the port axial direction is restricted by the intermediate diameter portion 122 .

The restricting portion 153 is formed in a tubular shape so as to protrude outward in the port axial direction from the inner peripheral portion of the holder tubular portion 151 . The restriction portion 153 restricts movement of the biasing member 132 in the port radial direction together with the holder cylinder portion 151 .

<Details of seal cylinder>
FIG. 7 is a perspective view of the seal cylinder member 131 with the valve sliding contact surface 141a facing upward. 8 is an end view of the seal cylinder member 131 viewed from the side of the valve slide contact surface 141a.
The seal cylinder member 131 has a first cylinder part 142 and a second cylinder part 141 having an outer diameter larger than that of the first cylinder part 142, and an axial end of the second cylinder part 141 (a The other end) is provided with a valve sliding contact surface 141 a that slidably contacts the outer peripheral surface of the peripheral wall portion 82 of the valve body 22 . A step surface 143 is provided between the outer peripheral surface of the first cylindrical portion 142 and the outer peripheral surface of the second cylindrical portion 141 . Also, the inner diameter of the first tubular portion 142 is formed smaller than the inner diameter of the second tubular portion 141 . A stepped surface 44 is provided between the inner peripheral surface of the first tubular portion 142 and the inner peripheral surface of the second tubular portion 141 .

The peripheral wall of the axial end (the inner end in the port axial direction) of the second cylindrical portion 141 has a projection height in the direction toward the peripheral wall portion 82 along the shape of the outer peripheral surface of the peripheral wall portion 82 of the valve body 22 . The width changes continuously in the circumferential direction. In other words, the peripheral wall of the axial end of the second cylindrical portion 141 continuously changes in protrusion height such that the valve sliding contact surface 141 a is in surface contact with the outer peripheral surface of the peripheral wall portion 82 of the valve body 22 . there is The axial end of the second cylindrical portion 141 has the lowest protrusion height in the outermost region with respect to the direction along the axis O1 (rotational axis of the valve body 22), and is perpendicular to the axis O1. With respect to (the direction along the rotation direction of the valve body 22), the protrusion height of the outermost region is the highest. 8 is a centerline indicating the center of the valve hole 96 (95, 97) in the direction of the axis O1 of the valve body 22. As shown in FIG.

The seal cylinder member 131 has a high protrusion height in the direction toward the peripheral wall part 82 of the valve body 22 (hereinafter referred to as "protrusion height in the direction of the valve body 22") of the peripheral wall of the second cylinder part 141. In two regions (two regions including a portion where the protrusion height in the direction of the valve body 22 is maximum), the length L from the axial center O3 of the seal cylinder member 131 to the outer peripheral surface is shorter than in other regions. A small outer diameter portion 55 is provided.

The small outer diameter portion 55 is formed by a plane P1 (first plane) having a linear shape substantially parallel to the rotation axis (axis O1) of the valve body 22 at the end on the side of the valve sliding contact surface 141a. In this embodiment, the plane P1 extends parallel to the axial center O3 of the seal cylinder member 131 .
In this embodiment, the inner peripheral surface of the second cylindrical portion 141 is formed in a circular shape with a constant length from the axis O3 over the circumferential direction. A second plane P2 (see FIG. 8) substantially parallel to the plane P1 (first plane) is formed by bulging radially inward in a portion of the peripheral surface where the protruding height in the direction of the valve body 22 is high. can be In this case, the radial width of the second cylindrical portion 141 can be made constant in the peripheral area of the seal cylindrical member 131 .

<How the control valve operates>
Next, a method of operating the above-described control valve 8 will be described.
As shown in FIG. 1 , in the main flow path 10 , the cooling water delivered by the water pump 3 undergoes heat exchange in the engine 2 and then flows toward the control valve 8 . As shown in FIG. 4, the cooling water that has passed through the engine 2 in the main flow path 10 flows into the connection flow path 92 inside the casing 21 through the inlet 37a.

A portion of the cooling water that has flowed into the connection flow path 92 flows into the EGR outlet 51 . The cooling water that has flowed into the EGR outlet 51 is supplied into the EGR flow path 14 through the EGR joint 52 . The cooling water supplied into the EGR flow path 14 is returned to the main flow path 10 after heat exchange between the cooling water and the EGR gas is performed in the EGR cooler 7 .

On the other hand, of the cooling water that has flowed into the connecting passage 92, the cooling water that has not flowed into the EGR outlet 51 flows into the flow passage 91 from the second side in the case axial direction. The cooling water that has flowed into the flow passage 91 is distributed to each outlet while flowing through the flow passage 91 in the axial direction of the case. That is, the cooling water flowing into the flow path 91 is distributed to the flow paths 11 to 13 through the outlets that communicate with the corresponding valve holes.

In order to switch the communication pattern between the valve hole and the outflow port in the control valve 8, the valve body 22 is rotated around the axis O1. By stopping the rotation of the valve body 22 at a position corresponding to the communication pattern to be set, the valve hole and the outflow port communicate with each other in the communication pattern corresponding to the stop position of the valve body 22 .

<Effects of Embodiment>
As described above, in the control valve 8 of the present embodiment, the axial center of the seal cylinder member 131 is provided in the region of the peripheral wall of the axial end portion of the seal cylinder member 131 where the projection height in the direction of the valve element 22 is high. A small outer diameter portion 55 having a shorter length from O3 to the outer peripheral surface than other regions is provided. Therefore, when the tubular seal member 131 is in a non-communicating state with the valve hole of the valve body 22, the region of the outer peripheral surface of the axial end portion of the tubular seal member 131 protruding in the direction of the valve body 22 has a high height. In addition, even if the hydraulic pressure in the casing 21 acts, a large moment is less likely to act on the tubular seal member 131 starting from the region where the projection height in the direction of the valve body 22 is low.

That is, in the control valve 8 of the present embodiment, the pressure receiving surface (small outer diameter portion 55) outside the high-protruding region of the seal cylinder member 131 in the direction of the valve body 22 is the starting point of the moment (the low-protruding region). ) is shortened, the moment acting on the other end of the seal cylinder member 131 is reduced. Therefore, it is possible to suppress deformation of the seal cylinder member 131 by the above-mentioned moment so that the region of the seal cylinder member 131 having a low projection height in the direction of the valve body 22 is lifted from the peripheral wall portion 82 of the valve body 22 . . Therefore, when the control valve of the present embodiment is adopted, the sealing performance between the seal cylinder member 131 and the valve body 22 can be enhanced.

Further, in the control valve 8 of the present embodiment, the small outer diameter portion 55 on the outer periphery of the seal cylinder member 131 is formed by a plane P1 (first plane), and the end of the plane P1 on the side of the valve sliding contact surface 141a is It has a linear shape substantially parallel to the rotation axis (axis O1) of the valve body 22 . Therefore, when the high protruding height region in the direction of the valve body 22 at the end of the seal cylinder member 131 receives the hydraulic pressure of the cooling water in the casing 21, the small outer diameter portion 55 (plane P1) forming a linear shape is in line contact with the peripheral wall portion 82 of the valve body 22 . Therefore, when this configuration is adopted, the contact range of the valve body 22 with the peripheral wall portion 82 is widened compared to the structure in which the end portion of the small outer diameter portion 55 makes point contact. The end of 131 becomes more difficult to wear.

Further, as described above, a second plane P2 substantially parallel to the plane P1 (first plane) forming the small outer diameter portion 55 is formed on the inner peripheral surface of the region of the seal cylinder member 131 having a high protrusion height in the direction of the valve body 22. is provided so as to bulge radially inward, the radial width of the valve sliding contact surface 141a of the seal cylinder member 131 can be made uniform in the circumferential direction. That is, even if the flat surface P1 is provided on the outer peripheral side of the seal cylinder member 131, the radial width of the valve sliding contact surface 141a of the seal cylinder member 131 is not narrowed partially in the circumferential direction. Therefore, when this configuration is adopted, the partial increase in the surface pressure due to the decrease in the radial width of the valve sliding contact surface 141a is suppressed, thereby preventing the valve from increasing in the area where the protrusion height in the direction of the valve body 22 is high. Wear of the sliding contact surface 141a can be suppressed.

Further, when the above configuration is applied to the present embodiment, the second plane P2 bulges inward and is provided radially inward of the second cylindrical portion 141 having an inner diameter larger than that of the first cylindrical portion 142. Become. In this case, the inner cross section of the second cylindrical portion 141 is narrowed by the bulge of the second plane P2. , the second plane P2 does not affect the flow rate of the cooling water. Therefore, in this case, it is possible to easily set and adjust the flow rate of the cooling water that flows out to the outlet.

[Second embodiment]
FIG. 9 is a perspective view of the tubular seal member 131A of the second embodiment, with the valve sliding contact surface 141Aa side facing upward, and FIG. is an end view. 11 is a cross-sectional view along line XI-XI in FIG. 10, and FIG. 12 is a cross-sectional view along line XII-XII in FIG.
131 A of seal cylinder members of this embodiment have the 1st cylinder part 142 and 141 A of 2nd cylinder parts with a larger outer diameter than the 1st cylinder part 142 like the seal cylinder member 131 of 1st Embodiment. . The first tubular portion 142 communicates with the outlet of the casing. A valve slide contact surface 141Aa that slidably contacts the outer peripheral surface of the peripheral wall of the valve body is provided at the axial end (the other axial end) of the second tubular portion 141A. The valve sliding contact surface 141Aa continuously changes in protrusion height along the outer surface of the peripheral wall portion of the valve body. Further, the radial width of the valve sliding contact surface 141Aa (the other end portion of the tubular seal member 142) is formed to have a constant width in the peripheral area of the tubular seal member 142. As shown in FIG.

The outer peripheral surface and inner peripheral surface of the first cylindrical portion 142 are formed in a perfect circular shape, while the outer peripheral surface and the inner peripheral surface of the second cylindrical portion 141A are formed in a substantially elliptical shape. . More specifically, the outer peripheral surface and the inner peripheral surface of the second cylindrical portion 141A have a substantially elliptical shape in which the region with the highest protrusion height in the valve body direction is the short diameter and the region with the lowest protrusion height is the major diameter. is formed in In this embodiment, the vicinity of the short diameter portion of the outer peripheral surface of the second cylindrical portion 141A is the small outer diameter portion 55A.

A step surface 143A is provided between the outer peripheral surface of the first cylindrical portion 142 and the outer peripheral surface of the second cylindrical portion 141A, as in the first embodiment. However, since the outer peripheral surface of the first cylindrical portion 142 has a perfect circular shape and the outer peripheral surface of the second cylindrical portion 141A has a substantially elliptical shape, the radial width of the stepped surface 143A is the difference between the two shapes. only varies in the circumferential direction.

A step surface 144A is provided between the inner peripheral surface of the first tubular portion 142 and the inner peripheral surface of the second tubular portion 141A. The radial width of the stepped surface 144A on the inner peripheral side is the difference between the inner peripheral surface of the perfectly circular first cylindrical portion 142 and the shape of the substantially elliptical second cylindrical portion 141A, similarly to the stepped surface 143A on the outer peripheral side. only varies in the circumferential direction. However, the stepped surface 144A does not exist at the portion corresponding to the region of the other end of the seal cylinder member 142 where the projecting height is the highest. In other words, the inner peripheral surface of the region with the highest protrusion height of the second cylindrical portion 141A is formed continuously with the inner peripheral surface of the first cylindrical portion 142 without steps.

The tubular seal member 131A of this embodiment differs in the outer surface shape of the second tubular portion 141A, but, similarly to the first embodiment, the axial end portion of the peripheral wall of the tubular seal member 131A in the valve element direction is A small outer diameter portion 55A is provided in a region having a high protrusion height. Therefore, when the hydraulic pressure in the casing acts on the area with a high projection height on the minor diameter side, a large moment acts on the tubular seal member 131A starting from the area with a low projection height in the direction of the valve body. become difficult. Therefore, also in the case of this embodiment, it is possible to improve the sealing performance between the seal cylinder member 131A and the valve body.

In addition, in the seal cylinder member 131A of the present embodiment, the outer peripheral surface of the second cylinder portion 141A is formed in a smooth, substantially elliptical shape. 141A is less likely to cause unnecessary turbulence in the flow of cooling water inside the casing.

Further, in the seal cylinder member 131A of the present embodiment, since the peripheral area of the second cylinder part 141A is formed to have a constant radial width, the narrowing of the radial width in the vicinity of the small outer diameter part 55A reduces valve sliding. A partial decrease in the contact surface pressure of the contact surface 141Aa can be suppressed.

In addition, in the seal cylinder member 131A of the present embodiment, the inner peripheral surface of the region with the highest protrusion height of the second tubular portion 141A is formed continuously with the inner peripheral surface of the first tubular portion 142 without steps. For this reason, in the seal cylinder member 131A of the present embodiment, there is a stepped portion that serves as a bending starting point between the inner peripheral surface of the region of the second tubular portion 141A having the highest protrusion height and the inner peripheral surface of the first tubular portion 142. not exist. Therefore, in the case of the present embodiment, even if a large hydraulic pressure acts on the outer peripheral surface near the protruding end of the region with the highest protruding height of the second cylindrical portion 141A, the first cylindrical portion 142 and the second cylindrical portion 141A Bending deformation is less likely to occur between them.

[Third embodiment]
FIG. 10 is a perspective view of the tubular seal member 131B of the third embodiment, with the valve sliding contact surface 141Ba facing upward, and FIG. is an end view.
The sealing tubular member 131B of this embodiment has a first tubular portion 142 and a second tubular portion 141B having an outer diameter larger than that of the first tubular portion 142 . The first cylindrical portion 142 is the same as in the first and second embodiments, but the second cylindrical portion 141B has a different shape.

As in the other embodiments, the second cylindrical portion 141B has a protrusion height at the end in the axial direction that continuously deforms along the outer surface shape of the peripheral wall portion of the valve body. The outer peripheral surface of the second cylindrical portion 141B has two regions with high protruding heights in the valve body direction (two regions including a portion with the highest protruding height in the valve body direction). A small outer diameter portion 55 having a shorter length L from the outer peripheral surface than the other regions is provided. As in the first embodiment, the small outer diameter portion 55 has an end on the side of the valve sliding contact surface 141Ba formed by a plane P1 (first plane) having a linear shape substantially parallel to the rotation axis (axis O1) of the valve body. formed. A second plane P2 substantially parallel to the plane P1 (first plane) bulges radially inward in a portion of the inner peripheral surface of the second cylindrical portion 141B having a high projection height in the valve body direction. is provided.

In addition, thick portions 60 are provided in two regions of the second cylindrical portion 141B having a low protrusion height in the valve body direction (two regions including the lowest protrusion height in the valve body direction). It is Each thick portion 60 is provided on the inner peripheral portion of the second cylindrical portion 141B so as to bulge radially inward. As shown in FIG. 11, the thick portions 60 arranged at the two positions are formed so as to be parallel to each other when the tubular seal member 131B is viewed from the axial direction (port axial direction). Linear inner edge portions opposed to each other are formed by the thick portion 60 on the inner side in the radial direction of the second cylindrical portion 141B. In the case of this embodiment, the thickest part of the thick part 60 is arranged at the lowest projecting height part of the end of the second cylindrical part 141B.

As in the other embodiments described above, the tubular seal member 131B of this embodiment has a small outer diameter in a region of the peripheral wall of the end portion in the axial direction of the tubular seal member 131B, where the protruding height in the direction of the valve element is high. A portion 55 is provided. Therefore, when the hydraulic pressure in the casing acts on the region with a high protrusion height, a large moment starting from the region with a low protrusion height in the direction of the valve body is less likely to act on the tubular seal member 131B. Therefore, also in the case of this embodiment, it is possible to improve the sealing performance between the seal cylinder member 131B and the valve body.

Further, the cylindrical seal member 131B of this embodiment has a plane P1 (first plane) forming the small outer diameter portion 55 on the inner peripheral surface of the region of the second cylindrical portion 141B having a high protruding height in the direction of the valve body. Since the parallel second plane P2 is provided so as to bulge radially inward, it is possible to suppress the narrowing of the radial width of the region of the second cylindrical portion 141B where the protrusion height is high. Therefore, it is possible to suppress wear of the valve sliding contact surface 141Ba in the region where the projection height of the second cylinder portion 141B is high.

Furthermore, in the seal cylinder member 131B of the present embodiment, the two regions of the second cylinder portion 141B having a low protruding height in the valve body direction have a radial width larger than the other regions on the circumference of the second cylinder portion 141B. A wide wall thickness 60 is provided. Therefore, the radial width of the valve sliding contact surface 14Aa is widened in the region where the projection height of the second tubular portion 141B is low. Therefore, it is possible to suppress an increase in the surface pressure in the region where the Hertzian surface pressure is most likely to increase when the cylindrical seal member 131B is pressed against the peripheral wall of the valve body (the region where the protrusion height is low). Therefore, when the tubular seal member 131B of the present embodiment is employed, it is possible to suppress early wear of the portion of the second tubular portion 141B having a low projection height.

The present invention is not limited to the above-described embodiments, and various design changes are possible without departing from the gist of the present invention.

8 control valve 21 casing 22 valve body 37a inlet 41b radiator outlet (outlet)
50 linear inner edge portion 55, 55A small outer diameter portion 56a warm air outlet (outlet)
66a air conditioning outlet (outlet)
82 Peripheral wall portion 95, 96, 97 Valve hole 131, 131A, 131B Seal tubular member 141, 141A, 141B Second tubular portion 141a, 141Aa, 141Ba Valve slide contact surface 142 First tubular portion O2 Axis center P1 Plane (first plane )
P2 second plane

Claims (6)

a casing having an inlet through which liquid flows from the outside and an outlet through which the liquid that has flowed inside flows out to the outside;
a valve element rotatably disposed inside the casing and having a peripheral wall portion formed with a valve hole communicating between the inside and the outside;
One end in the axial direction communicates with the outflow port, and the other end in the axial direction slides on the outer peripheral surface of the peripheral wall portion at a position where at least a part of the rotation path of the valve hole of the valve body overlaps. a seal cylinder member provided with a valve sliding contact surface that movably abuts,
In a control valve in which the other axial end portion of the seal cylinder member protrudes continuously in the circumferential direction along the shape of the outer peripheral surface of the peripheral wall portion in the direction toward the peripheral wall portion,
In a region of the outer peripheral surface of the peripheral wall of the other end portion of the seal cylinder member, the length from the axial center of the seal cylinder member to the outer peripheral surface is shorter than the other regions in a region with a high protrusion height. An outer diameter is provided ,
The small outer diameter portion has a first flat surface having an end portion on the side of the valve sliding contact surface that forms a linear shape substantially parallel to the rotation axis of the valve body,
A second plane substantially parallel to the first plane bulges radially inward of the tubular seal member on the inner peripheral surface of the region of the peripheral wall of the other end portion of the tubular seal member, the second plane being substantially parallel to the first plane. A control valve, characterized in that it is formed by The seal cylinder member is
a first cylindrical portion located on the one end side and communicating with the outflow port;
a second tubular portion located on the other end side, the axial end surface of which constitutes the valve sliding contact surface, and the second cylindrical portion formed by bulging the second flat surface on the inner peripheral surface;
3. The control valve according to claim 2 , wherein the inner diameter of said first tubular portion is smaller than the inner diameter of said second tubular portion. a casing having an inlet through which liquid flows from the outside and an outlet through which the liquid that has flowed inside flows out to the outside;
a valve element rotatably disposed inside the casing and having a peripheral wall portion formed with a valve hole communicating between the inside and the outside;
One end in the axial direction communicates with the outflow port, and the other end in the axial direction slides on the outer peripheral surface of the peripheral wall portion at a position where at least a part of the rotation path of the valve hole of the valve body overlaps. a seal cylinder member provided with a valve sliding contact surface that movably abuts,
In a control valve in which the other axial end portion of the seal cylinder member protrudes continuously in the circumferential direction along the shape of the outer peripheral surface of the peripheral wall portion in the direction toward the peripheral wall portion,
In a region of the outer peripheral surface of the peripheral wall of the other end portion of the seal cylinder member, the length from the axial center of the seal cylinder member to the outer peripheral surface is shorter than the other regions in a region with a high protrusion height. An outer diameter is provided,
The outer peripheral surface of the peripheral wall of the other end portion of the seal cylinder member is formed in a substantially elliptical shape in which the region with the highest protruding height is the short diameter and the region with the lowest protruding height is the major diameter. and control valve . 4. The control valve according to claim 3 , wherein the radial width of the other end portion of the tubular seal member is constant in the peripheral area of the tubular seal member. The seal cylinder member is
a first cylindrical portion located on the one end side and communicating with the outflow port;
a second cylindrical portion positioned on the other end side and having an axial end surface forming the valve sliding contact surface;
The outer peripheral surface and the inner peripheral surface of the peripheral wall of the second cylindrical portion are formed in a substantially elliptical shape in which the area with the highest protrusion height is the minor axis and the area with the lowest protrusion height is the major axis,
5. The method according to claim 3 or 4 , wherein the inner peripheral surface of the region of the second cylindrical portion having the highest protrusion height is formed continuously without a step on the inner peripheral surface of the first cylindrical portion. Control valve as described. 1 to 1, characterized in that the radial width of the low-protrusion-height region of the other end is formed to be wider than the radial-direction width of the high-protrusion-height region of the other end. 6. The control valve according to any one of 5 .

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