CN113167393A - Control valve - Google Patents

Abstract

A control valve is provided with a housing, a valve body, and a seal tube member (131). The housing has an inflow port and an outflow port. The valve body is rotatably disposed in the housing and has a peripheral wall portion in which a valve hole for communicating the inside and the outside is formed. One end of the seal cylinder member (131) communicates with the outlet port, and the other end is provided with a valve sliding contact surface (141 a). The protruding height of the other end of the seal cylinder member (131) changes continuously in the circumferential direction along the shape of the outer peripheral surface of the peripheral wall portion. In the region of the other end of the seal cylindrical member (131) where the projection height is high, a small outer diameter section (55) is provided in which the length (L) from the axis of the seal cylindrical member (131) to the outer peripheral surface is shorter than in other regions.

Description

Control valve

Technical Field

The present invention relates to a control valve used for switching a flow path of cooling water for a vehicle.

The present application claims priority based on japanese patent application No. 2019-.

Background

In a cooling system for cooling an engine using cooling water, a bypass flow path bypassing a radiator, a warm-up flow path passing through an oil heater (oil heater), and the like may be provided in addition to a radiator flow path circulating between the radiator and the engine. In such a cooling system, a control valve is interposed at a branch portion of the flow path, and the flow path is appropriately switched by the control valve. As a control valve, a control valve is known in which a cylindrical valve body is rotatably disposed in a housing (case), and an arbitrary flow path is opened or closed according to a rotational position of the valve body (for example, see patent document 1).

The control valve described in patent document 1 includes an inlet port into which a liquid such as cooling water flows and a plurality of outlet ports through which the liquid flowing into the inlet port flows to the outside. A plurality of valve holes for communicating the inside and the outside are formed in the peripheral wall of the valve body so as to correspond to the plurality of outlet ports. One end side of a substantially cylindrical seal tube member is slidably held at each outlet port. One end of each seal cylinder member communicates with the downstream side of the corresponding outlet port. Further, a valve sliding contact surface that slidably comes into contact with the outer peripheral surface of the valve body is provided at the other end portion of each seal cylinder member. 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 overlapping the rotational path of the corresponding valve hole of the valve body.

Further, the valve sliding contact surface of the seal cylinder member is formed so as to follow the outer surface shape of the valve body in close contact with the outer peripheral surface of the valve body. That is, the height of the other end portion of the seal cylindrical member in the axial direction protruding in the valve body direction is continuously changed in the circumferential direction of the seal cylindrical member so as to follow the outer surface shape of the valve body.

The valve body of the control valve allows the liquid to flow out from the inner area of the valve body to the corresponding outlet port when the sealing cylinder member is located at a position communicating with the corresponding valve hole, and blocks the liquid from flowing out from the inner area of the valve body to the corresponding outlet port when the sealing cylinder member is located at a position not communicating with the corresponding valve hole. Further, the rotational position of the valve body is operated by an actuator such as an electric motor.

Documents of the prior art

Patent document

Patent document 1: japanese patent laid-open publication No. 2017-3064

Disclosure of Invention

Problems to be solved by the invention

In the above-described conventional control valve, the projecting height of the other end portion of the seal cylindrical member continuously changes so as to follow the outer surface shape of the cylindrical valve element. Therefore, in the region where the projection height in the other end portion of the seal cylindrical member is high, when the pressure of the liquid inside the housing acts on the outer circumferential surface in the vicinity of the projection end, the pressure acts as a moment that causes the other end portion side of the seal cylindrical member to be flexurally deformed. Specifically, when the pressure of the liquid in the housing acts on the outer peripheral surface near the projecting end in the region where the projecting height of the other end portion of the seal cylinder member is high, a force due to the pressure acting on the outer peripheral surface acts as a moment starting from the region where the projecting height of the other end portion of the seal cylinder member is low, and the region where the projecting height of the seal cylinder member is low is deformed so as to be separated from the peripheral wall of the valve body. Therefore, there is a fear that a gap between a region where the protruding height of the seal cylinder member is low and the peripheral wall portion of the valve body increases when the pressure inside the housing becomes high.

The problem to be solved is to improve the sealing performance between a seal cylinder member and a valve body by suppressing deformation of the seal cylinder member due to hydraulic pressure in a housing.

Means for solving the problems

A control valve according to an aspect of the present invention includes: a housing having an inlet through which liquid flows from outside and an outlet through which the liquid flowing into the housing flows out to outside; a valve body which is rotatably disposed in the housing and has a peripheral wall portion in which a valve hole for communicating the inside and the outside is formed; and a seal cylinder member having one axial end portion communicating with the outlet port and a valve sliding contact surface provided at the other axial end portion so as to slidably contact an outer peripheral surface of the peripheral wall portion at a position overlapping at least a part of a rotation path of the valve hole of the valve body, wherein a projection height of the other axial end portion of the seal cylinder member in a direction to the peripheral wall portion continuously changes in a circumferential direction along a shape of the outer peripheral surface of the peripheral wall portion, and wherein a small outer diameter portion having a length from an axial center to the outer peripheral surface of the seal cylinder member shorter than other regions is provided in a region where the projection height of the other axial end portion of the seal cylinder member is high.

With the above configuration, when the other end portion in the axial direction of the seal cylinder member is closed by the outer peripheral surface of the peripheral wall portion of the valve body, the outflow of the 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 end portion in the axial direction of the seal cylindrical member communicates with (overlaps with) the valve hole of the valve body, the liquid flows out from the inside of the valve body to the outlet port. When the other end portion in the axial direction of the seal cylinder member is closed by the outer peripheral surface of the peripheral wall portion of the valve body, the valve sliding contact surface of the seal cylinder member is pressed against the peripheral wall portion of the valve body. At this time, the pressure of the liquid in the housing acts on the outer periphery of the other end portion of the seal cylinder member. In the region where the protruding height of the other end portion of the seal cylinder member is high, a force caused by the pressure of the liquid inside the housing acts on the outer peripheral surface in the vicinity of the protruding end. The force acts on the other end side of the seal tube member as a moment starting from a region where the projection height is low. However, in the control valve of the present invention, since the small outer diameter portion is provided in the region where the projection height is high in the other end portion of the seal cylindrical member, the distance from the pressure receiving surface (small outer diameter portion) of the region where the projection height is high to the start point of the moment becomes short. As a result, the moment acting on the other end portion of the seal cylindrical member becomes small, and the flexural deformation of the other end portion of the seal cylindrical member due to the moment is suppressed.

The small outer diameter portion may be formed by a 1 st plane having a linear shape substantially parallel to the rotation axis of the valve body at an end on the valve sliding contact surface side.

In this case, when a region in which the projection height in the other end portion of the seal cylinder member is high is subjected to the hydraulic pressure inside the housing, the end portion of the small outer diameter portion in a linear shape comes into line contact with the peripheral wall portion of the valve body. Therefore, the contact range with the outer surface of the valve body is wider than that in the case where the outer surface of the circular arc shape makes point contact with the peripheral wall portion of the valve body. As a result, the abrasion of the other end portion of the seal cylinder member is further suppressed.

A 2 nd plane substantially parallel to the 1 st plane may be formed on an inner peripheral surface of a region of the other end portion of the tubular seal member having a high projection height so as to bulge inward in a radial direction of the tubular seal member.

In this case, since the width (thickness) in the radial direction of the region where the protruding height of the other end portion of the seal cylindrical member is high can be made substantially constant, an increase in the surface pressure due to a decrease in the radial width of the valve sliding contact surface can be suppressed. As a result, the abrasion of the other end portion of the seal cylinder member can be further suppressed.

The seal cylinder member may include: a 1 st cylinder part located on the one end side and communicating with the outlet port; and a 2 nd cylinder portion located on the other end portion side, an end surface in an axial direction constituting the valve sliding contact surface, and an inner peripheral surface bulging to form the 2 nd plane, wherein an inner diameter of the 1 st cylinder portion is formed smaller than an inner diameter of the 2 nd cylinder portion.

In this case, the flow rate of the liquid flowing out to the downstream side of the outlet port through the seal cylinder member is determined by the inner diameter of the 1 st cylinder portion of the seal cylinder member having a relatively small inner diameter. The 2 nd plane formed so as to bulge toward the inner peripheral side is provided radially inside the 2 nd cylindrical portion having a relatively large inner diameter, and therefore, the flow rate of the liquid flowing out to the downstream side of the outlet port is not affected. Therefore, when the present configuration is adopted, the flow rate of the liquid flowing out to the outlet port can be easily set and adjusted.

The outer peripheral surface of the other end portion of the seal cylinder member may be formed in a substantially elliptical shape having a short diameter in a region having the highest projection height and a long diameter in a region having the lowest projection height.

In this case, the outer peripheral surface of the other end portion of the seal cylindrical member smoothly changes in a substantially elliptical shape, and therefore the other end portion of the seal cylindrical member is less likely to generate unnecessary turbulence in the flow in the housing.

The radial width of the other end portion of the tubular seal member may be formed to be a constant width in the circumferential range of the tubular seal member.

In this case, an increase in the surface pressure due to a local decrease in the radial width of the valve sliding contact surface can be suppressed. As a result, the abrasion of the other end portion of the seal cylinder member can be further suppressed.

The seal cylinder member may include: a 1 st cylinder part located on the one end side and communicating with the outlet port; and a 2 nd cylindrical portion located on the other end side, an axial end surface of the 2 nd cylindrical portion constituting the valve sliding contact surface, an outer peripheral surface and an inner peripheral surface of the 2 nd cylindrical portion being formed in a substantially elliptical shape in which a region having a highest projecting height is a short diameter and a region having a lowest projecting height is a long diameter, and an inner peripheral surface of the 2 nd cylindrical portion in the region having the highest projecting height is continuously formed without a step from the inner peripheral surface of the 1 st cylindrical portion.

In this case, since there is no stepped portion serving as a bending start point between the inner peripheral surface of the region of the 2 nd cylindrical portion having the highest projecting height and the inner peripheral surface of the 1 st cylindrical portion, even if the hydraulic pressure in the housing acts on the outer peripheral surface in the vicinity of the projecting end of the region of the 2 nd cylindrical portion having the highest projecting height, bending deformation is less likely to occur between the 1 st cylindrical portion and the 2 nd cylindrical portion.

The width in the radial direction of the region having the lower projecting height of the other end portion may be larger than the width in the radial direction of the region having the higher projecting height of the other end portion.

In this case, the width in the radial direction of the region where the protrusion height is low where the hertzian surface pressure tends to increase in the other end portion of the seal cylinder member is formed wide, and therefore the increase in the surface pressure of the portion where the protrusion height is low can be suppressed. Thus, premature wear of the portion of the other end portion of the seal cylinder member where the projection height is low can be suppressed.

Effects of the invention

In the control valve, the small outer diameter portion having a length from the axial center of the seal cylindrical member to the outer peripheral surface shorter than the other region is provided in the region of the other end portion of the seal cylindrical member having a high projection height, so that the generation of moment due to the hydraulic pressure applied to the outer peripheral surface of the region of the high projection height can be suppressed, and the deflection deformation of the other end portion of the seal cylindrical member can be suppressed. Therefore, when the control valve is used, the sealing performance between the seal cylinder member and the valve body can be improved.

Drawings

Fig. 1 is a block diagram of a cooling system of an embodiment.

Fig. 2 is a perspective view of the control valve of embodiment 1.

Fig. 3 is an exploded perspective view of the control valve of embodiment 1.

Fig. 4 is a sectional view taken along line IV-IV of fig. 2.

Fig. 5 is an enlarged view along line V-V of fig. 2.

Fig. 6 is an enlarged view of a VI portion of fig. 5.

Fig. 7 is a perspective view of a seal cylinder member according to embodiment 1.

Fig. 8 is an end view of the seal cylinder member of embodiment 1.

Fig. 9 is a perspective view of a seal cylinder member according to embodiment 2.

Fig. 10 is an end view of the seal cylinder member of embodiment 2.

Fig. 11 is a sectional view of the seal cartridge member of embodiment 2 taken along line XI-XI of fig. 10.

Fig. 12 is a sectional view of the seal cylinder member of embodiment 2 taken along line XII-XII in fig. 10.

Fig. 13 is a perspective view of a seal cylinder member according to embodiment 3.

Fig. 14 is an end view of the seal cylinder member of embodiment 3.

Detailed Description

Embodiments of the present invention will be described below with reference to the drawings. In the following description, a case will be described in which the control valve of the present embodiment is employed in a cooling system that cools an engine using cooling water. In each embodiment, the same portions are denoted by the same reference numerals, and redundant description thereof is omitted.

< Cooling System >

Fig. 1 is a block diagram of a cooling system 1.

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, an electric hybrid vehicle, or the like, in addition to a vehicle having only an engine.

The cooling system 1 is configured by connecting 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 valve 8(EWV) by various flow paths 10 to 14.

The water pump 3, the engine 2, and the control valve 8 are connected in this order from upstream to downstream in 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 by the operation of the water pump 3.

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

The radiator flow path 11 is connected to the radiator 4. The radiator flow path 11 performs heat exchange between the cooling water and the outside air in the radiator 4.

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

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

The EGR passage 14 is connected to the EGR cooler 7. The EGR passage 14 exchanges heat between the cooling water and the EGR gas in the EGR cooler 7.

In the cooling system 1 described above, the cooling water having passed through the engine 2 in the main flow path 10 flows into the control valve 8, and is then selectively distributed to the various flow paths 11 to 13 by the operation of the control valve 8. This enables early temperature rise, high water temperature (optimum temperature) control, and the like, thereby improving the fuel efficiency of the vehicle.

< control valve >

Fig. 2 is a perspective view of the control valve 8 of embodiment 1. Fig. 3 is an exploded perspective view of the control valve 8.

As shown in fig. 2 and 3, the control valve 8 mainly includes a housing 21, a valve body 22 (see fig. 3), and a drive unit 23.

< outer case >

The housing 21 includes a cylindrical housing main body 25 having a bottom, and a lid 26 for closing an opening of the housing main body 25. In the following description, the direction along the axis O1 of the outer shell 21 will be simply referred to as the shell axial direction. In the case axial direction, a direction toward the bottom wall portion 32 of the case main body 25 with respect to the case peripheral wall 31 of the case main body 25 is referred to as a 1 st side, and a direction toward the lid 26 with respect to the case peripheral wall 31 of the case main body 25 is referred to as a 2 nd side. The direction perpendicular to the axis O1 is referred to as the shell radial direction, and the direction about the axis O1 is referred to as the shell circumferential direction.

The case peripheral wall 31 of the case main body 25 is formed with a plurality of attachment pieces 33. The fitting pieces 33 project outward in the shell radial direction from the shell peripheral wall 31. The control valve 8 is fixed to the engine room via, for example, each fitting piece 33. The position, number, and the like of each mounting piece 33 can be appropriately changed.

Fig. 4 is a sectional view taken along line IV-IV of fig. 2.

As shown in fig. 3 and 4, an inflow port 37 bulging outward in the shell radial direction is formed in a portion of the shell circumferential wall 31 on the 2 nd side. An inlet port 37a (see fig. 4) is formed in the inlet port 37 so as to penetrate the inlet port 37 in the shell radial direction. The inlet 37a communicates the inside and outside of the housing 21. The main channel 10 (see fig. 1) is connected to an opening end surface (an outer end surface in the shell radial direction) of the inflow port 37.

As shown in fig. 4, a radiator port 41 that projects outward in the shell radial direction is formed in the shell peripheral wall 31 at a position that faces the inlet port 37 in the shell radial direction with an axis O1 therebetween. A failure (fail) opening 41a and a radiator outlet 41b (outlet) are formed in the radiator port 41 in parallel in the shell axial direction. The failure opening 41a and the radiator outlet port 41b penetrate the radiator port 41 in the case radial direction, respectively. In the present embodiment, the failure opening 41a is opposed to the inflow port 37a described above in the shell radial direction. The radiator outlet 41b is located on the 1 st side in the housing axial direction with respect to the failure opening 41 a.

A radiator joint 42 is connected to an opening end face (an outer end face in the case radial direction) of the radiator port 41. The radiator joint 42 connects the radiator port 41 and the upstream end portion of the radiator flow path 11 (see fig. 1). Further, the radiator joint 42 is welded (e.g., vibration welded or the like) to the opening end face of the radiator port 41.

A thermostat 45 is provided in the failure opening 41 a. The thermostat 45 is opposed to the inflow port 37a in the shell radial direction. The thermostat 45 opens or closes the malfunction opening 41a according to the temperature of the cooling water flowing in the housing 21.

An EGR flow outlet 51 is formed in a portion of the cover 26 that is located at a position offset from the radiator port 41 in the case radial direction with respect to the axis O1. The EGR flow outlet 51 penetrates the lid 26 in the case axial direction. In the present embodiment, the EGR flow outlet 51 intersects (is orthogonal to) the opening direction (the shell radial direction) of the failure opening 41 a. Further, at least a part of the EGR flow outlet 51 overlaps the thermostat 45 in a front view viewed from the housing axial direction.

An EGR joint 52 is formed at an opening edge of the EGR flow outlet 51 of the lid body 26. The EGR joint 52 is formed in a tubular shape extending outward in the housing radial direction as going to the 2 nd side in the housing axial direction, and connects the EGR flow outlet 51 to the upstream end of the EGR flow passage 14 (see fig. 1).

As shown in fig. 3, a warm-up port 56 that bulges outward in the shell radial direction is formed in the shell peripheral wall 31 at a portion located on the 1 st side in the shell axial direction with respect to the radiator port 41. A warm-up oil outlet 56a (oil outlet) that penetrates the warm-up port 56 in the shell radial direction is formed in the warm-up port 56. A warming-up joint 62 is connected to an opening end surface of the warming-up port 56. The warm-up joint 62 connects the warm-up port 56 to the upstream end of the warm-up flow path 12 (see fig. 1). Further, the warm-up joint 62 is welded (for example, vibration welded or the like) to the opening end face of the warm-up port 56.

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

< drive Unit >

As shown in fig. 2, the drive unit 23 is mounted to the bottom wall portion 32 of the case main body 25. In the drive unit 23, a motor, a speed reduction mechanism, a control board, and the like, which are not shown, are housed in a unit case.

< rotor >

As shown in fig. 3 and 4, the valve body 22 is accommodated in the housing 21. The valve element 22 is formed in a cylindrical shape, and is disposed inside the housing 21 coaxially with the axis O1 of the housing 21. The valve body 22 opens or closes the above-described outlet ports (the radiator outlet port 41b, the warm-air outlet port 56a, and the air-conditioner outlet port 66a) by rotating about the axis O1.

As shown in fig. 4, the valve body 22 is configured such that the inner shaft portion 73 is insert-molded inside the rotor body 72. The inner shaft portion 73 extends coaxially with the axis O1.

The 1 st end of the inner shaft 73 passes through the bottom wall 32 in the housing axial direction through a through hole (atmosphere opening portion) 32a formed in the bottom wall 32. The 1 st end of the inner shaft 73 is rotatably supported by the 1 st bushing (1 st bearing) 78 provided in the bottom wall 32. Specifically, a 1 st shaft accommodating wall 79 is formed on the 2 nd side of the bottom wall portion 32 in the housing axial direction. The 1 st shaft accommodating wall 79 surrounds the through hole 32 a. The 1 st bushing 78 described above is fitted inside the 1 st shaft accommodating wall 79.

A coupling portion 73a is formed at a portion of the inner shaft portion 73 located on the 1 st side in the housing axial direction with respect to the 1 st bushing 78 (a portion located on the outer side with respect to the bottom wall portion 32). The coupling portion 73a is coupled to the drive unit 23 described above outside the housing 21. Thereby, the power of the drive unit 23 is transmitted to the inner shaft portion 73.

The 2 nd end of the inner shaft 73 is rotatably supported by the 2 nd bushing (2 nd bearing) 84 provided in the cover 26. Specifically, the cover 26 has a 2 nd shaft accommodating wall 86 formed on the 1 st side in the housing axial direction. The 2 nd shaft accommodating wall 86 surrounds the axis O1 at a position radially inward of the EGR flow outlet 51 with respect to the housing. The 2 nd bushing 84 is fitted inside the 2 nd shaft accommodating wall 86.

The rotor body 72 surrounds the inner shaft 73. The rotor body 72 includes an outer shaft portion 81 covering the inner shaft portion 73, a peripheral wall portion 82 surrounding the outer shaft portion 81, and spokes 83 connecting 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 in a state where both ends of the inner shaft portion 73 in the shell axial direction are exposed. In the present embodiment, the outer shaft 81 and the inner shaft 73 constitute a rotary shaft 85 of the valve body 22.

In the 1 st shaft accommodating wall 79 described above, a 1 st lip seal 87 is provided at a portion on the 2 nd side in the shell axial direction with respect to the 1 st bush 78. The 1 st lip seal 87 seals between the inner peripheral surface of the 1 st shaft accommodating wall 79 and the outer peripheral surface of the rotating shaft 85 (outer shaft portion 81). In the 1 st shaft accommodating wall 79, a portion located on the 1 st side in the housing axial direction from the 1 st lip seal 87 is opened to the atmosphere through the through hole 32 a.

On the other hand, in the 2 nd shaft accommodating wall 86, a 2 nd lip seal 88 is provided in a portion located on the 1 st side in the housing axial direction with respect to the 2 nd bush 84. The 2 nd lip seal 88 seals between the inner peripheral surface of the 2 nd shaft accommodating wall 86 and the outer peripheral surface of the rotating shaft 85 (outer shaft portion 81). The lid 26 is formed with a through hole (atmosphere opening portion) 98 penetrating the lid 26 in the housing axial direction.

The peripheral wall portion 82 of the valve body 22 is disposed coaxially with the axis O1. The peripheral wall portion 82 is disposed in the housing 21 at a position closer to the 1 st side in the housing axial direction than the inlet 37 a. Specifically, the peripheral wall 82 is disposed at a position across the radiator outlet 41b, the warm-air outlet 56a, and the air-conditioning outlet 66a while avoiding the failure opening 41a in the case axial direction. The inner side of the peripheral wall portion 82 forms a flow passage 91 through which the cooling water flowing into the casing 21 through the inlet 37a flows in the casing axial direction. On the other hand, a portion of the casing 21 located on the 2 nd side in the casing axial direction with respect to the peripheral wall portion 82 constitutes a connection flow path 92 communicating with the flow passage 91. Further, a clearance C2 is provided in the shell radial direction between the outer peripheral surface of the peripheral wall portion 82 and the inner peripheral surface of the shell peripheral wall 31.

The peripheral wall portion 82 is formed with a valve hole 95 penetrating the peripheral wall portion 82 in the case radial direction at the same position in the case axial direction as the above-described radiator outlet 41 b. When at least a part of the valve hole 95 overlaps the seal tube member 131 inserted into the radiator outlet port 41b when viewed in the radial direction of the case, the inside of the peripheral wall portion 82 (the flow passage 91) communicates with the radiator outlet port 41b through the valve hole 95.

In the peripheral wall portion 82, another valve hole 96 penetrating the peripheral wall portion 82 in the shell radial direction is formed at the same position in the shell axial direction as the warm air outlet 56a described above. When at least a part of the valve hole 96 overlaps the seal cylindrical member 131 inserted into the warm air outlet port 56a when viewed in the casing radial direction, the valve hole 96 allows the inside of the peripheral wall portion 82 (the flow passage 91) to communicate with the warm air outlet port 56 a.

The peripheral wall portion 82 is further formed with another valve hole 97 penetrating the peripheral wall portion 82 in the shell radial direction at the same position in the shell axial direction as the air-conditioning outlet 66a described above. When at least a part of the valve hole 97 overlaps the seal cylindrical member 131 inserted into the air-conditioning outlet port 66a when viewed in the radial direction of the casing, the interior of the peripheral wall portion 82 (the flow passage 91) communicates with the air-conditioning outlet port 66a via the valve hole 97.

The valve body 22 switches communication and blocking between the valve holes 95, 96, 97 and the outlet ports 41b, 56a, 66a corresponding to these valve holes in accordance with rotation about the axis O1. Further, the communication mode of the valve holes 95, 96, 97 and the outlet ports 41b, 56a, 66a can be appropriately set.

Next, details of a connection portion of the warming-up port 56 and the warming-up joint 62 will be described. Note that the connection portion between the radiator port 41 and the radiator joint 42 and the connection portion between the air-conditioning port 66 and the air-conditioning joint 68 have the same configuration as the connection portion between the warm-up port 56 and the warm-up joint 62, and therefore, the description thereof is omitted.

Fig. 5 is an enlarged sectional view corresponding to line V-V of fig. 2. In the following description, a direction along the axis O2 of the warm air outlet 56a may be referred to as a port axial direction (1 st direction). In this case, in the port axial direction, a direction toward the axis O1 with respect to the warm-up port 56 is referred to as an inner side, and a direction away from the axis O1 with respect to the warm-up port 56 is referred to as an outer side. The direction perpendicular to the axis O2 is sometimes referred to as the port radial direction (2 nd direction), and the direction about the axis O2 is sometimes referred to as the port circumferential direction.

As shown in fig. 5, the warming-up port 56 has a seal cylinder portion 101 extending in the port axial direction and a port flange portion 102 projecting outward in the port radial direction from the seal cylinder portion 101. The inside of the seal tube portion 101 constitutes the warm air outflow port 56a (outflow port). In the present embodiment, the inner diameter of the seal cylinder portion 101 is set to be the same in a region other than the outer end portion in the port axial direction.

A surrounding wall 105 protruding 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 around the entire circumference of the port flange portion 102. A port engagement portion 106 protruding outward in the port axial direction is formed in the port flange portion 102 at a portion located inward in the port radial direction with respect to the surrounding wall 105. The port engagement portion 106 is formed on the entire circumference of the port flange portion 102.

The warm-up joint 62 includes a joint tube portion 110 disposed coaxially with the axis O2, and a joint flange portion 111 projecting outward in the port radial direction from an inner end portion in the port axial direction of the joint tube portion 110.

The joint flange portion 111 is formed in an annular shape having the same outer diameter as the port flange portion 102 and having an inner diameter larger than the outer diameter of the seal cylinder portion 101. A joint engaging portion 113 protruding inward in the port axial direction is formed on an inner peripheral portion of the joint flange portion 111. The joint engaging portion 113 is opposite to the port engaging portion 106 in the port axial direction. The warm-up port 56 and the warm-up joint 62 are joined to each other by the opposite faces of the port joint portion 106 and the joint portion 113 being vibration-welded to each other.

The joint cylinder portion 110 extends outward in the axial direction of the port from the inner peripheral edge of the joint flange portion 111. The joint cylinder portion 110 is formed in a multi-stage cylindrical shape having a diameter gradually reduced toward the outside in the axial direction of the port. Specifically, the large diameter portion 121, the medium diameter portion 122, and the small diameter portion 123 of the joint cylinder portion 110 are connected in this order outward in the port axial direction.

The large diameter portion 121 surrounds the seal cylinder portion 101 with a space outward in the port radial direction with respect to the seal cylinder portion 101. The intermediate diameter portion 122 is opposed to the seal cylinder 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 cylinder member 131, a force application member 132, a seal ring 133, and a holder (holder) 134. As shown in fig. 3, a seal mechanism 130 having the same configuration 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. In the description of the present embodiment, the sealing 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 sealing mechanism 130 provided in the warm-up port 56, and the description thereof is omitted.

As shown in fig. 5, the tubular seal member 131 is inserted into the warm air outflow port 56 a. The seal cylinder member 131 has a peripheral wall extending coaxially with the axis O2. The peripheral wall of the seal cylindrical member 131 is formed in a multi-stage cylindrical shape having a stepwise reduced outer diameter as going outward in the port axial direction. Specifically, the peripheral wall of the seal cylinder member 131 includes: a 1 st cylinder portion 142 located outside (one end side in the axial direction) in the port axial direction and communicating with the downstream side of the warm-up oil outlet 56 a; and a 2 nd cylindrical portion 141 located on the inner side in the axial direction of the port (the other end side in the axial direction), and having an inner diameter and an outer diameter larger than those of the 1 st cylindrical portion 142.

The 2 nd cylindrical portion 141 having a large diameter of the cylindrical seal member 131 is slidably inserted into the inner peripheral surface of the cylindrical seal portion 101. The inner end surface in the port axial direction of the 2 nd cylindrical portion 141 constitutes a valve sliding contact surface 141a which slidably abuts against the outer peripheral surface of the peripheral wall portion 82 of the valve body 22. In the present embodiment, the valve sliding surface 141a is a curved surface formed following the radius of curvature of the outer peripheral surface of the peripheral wall portion 82.

The outer peripheral surface of the 1 st cylindrical portion 142 is continuous with the outer peripheral surface of the 2 nd cylindrical portion 141 via the stepped surface 143. The step surface 143 is inclined outward in the port radial direction as it goes inward in the port axial direction, and then extends outward in the port radial direction. Therefore, a seal gap Q2 is provided in the port radial direction between the outer peripheral surface of the small-diameter 1 st cylinder portion 142 and the inner peripheral surface of the seal cylinder portion 101.

An outer end surface (hereinafter referred to as a "seat surface 142 a") of the 1 st cylinder portion 142 in the port axial direction is a flat surface perpendicular to the port axial direction. The seat surface 142a of the 1 st cylinder portion 142 is disposed at the same position as the outer end surface of the seal cylinder portion 101 in the port axial direction. Further, the seal cylinder member 131 is separated from the warming-up joint 62 in the port radial direction and the port axial direction.

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

The seal ring 133 is, for example, a Y-shaped gasket. The seal ring 133 is inserted around the 1 st cylinder portion 142 of the seal cylinder member 131 with the opening (bifurcated portion) directed inward in the port axial direction. Specifically, in a state where the seal ring 133 is disposed in the seal gap Q2, the distal ends of the bifurcated portions of the seal ring 133 are slidably in close contact with the outer peripheral surface of the 1 st tube portion 142 and the inner peripheral surface of the seal tube portion 101. In the seal gap Q2, the hydraulic pressure of the cooling water in the housing 21 is introduced into a region on the inside in the port axial direction of the seal ring 133 through the gap between the inner peripheral surface of the seal tube portion 101 and the 2 nd tube portion 141 of the seal tube member 131. The step surface 143 is formed in the port axial direction in an opposite direction to the valve sliding contact surface 141a of the seal cylinder member 131. The stepped surface 143 constitutes a pressure receiving surface that is pressed inward in the port axial direction by the hydraulic pressure of the cooling water in the housing 21.

Fig. 6 is an enlarged view of a VI portion of fig. 5.

Here, in the tubular seal 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: the pressure reduction constant of the cooling water flowing through the minute gap between the valve sliding contact surface 141a and the peripheral wall 82 of the valve body 22

α: lower limit of pressure reduction constant determined by physical properties of cooling water

Further, the area S1 of the step surface 143 and the area S2 of the valve sliding contact surface 141a are areas when projected in the port axial direction.

α in the formula (2) is a standard value of the pressure decrease constant determined by the type of the cooling water, the use environment (for example, temperature), and the like. For example, under normal use conditions, α is 1/2 in the case of water. When the physical properties of the cooling water used have changed, the change is α 1/3 or the like.

The pressure reduction constant k in expression (2) is α (e.g., 1/2) which is a standard value of the pressure reduction constant when the valve sliding contact surface 141a uniformly contacts the peripheral wall portion 82 from the outer edge to the inner edge in the port radial direction. However, due to manufacturing errors, assembly errors, or the like of the tubular seal member 131, a gap between the outer peripheral portion of the valve sliding contact surface 141a and the peripheral wall portion 82 may slightly increase relative to the inner peripheral portion of the valve sliding contact surface 141 a. In this case, the pressure decrease constant k in the formula (2) gradually approaches k to 1.

In the present embodiment, the relationship between the areas S1, S2 of the stepped surface 143 and the valve sliding-contact surface 141a is determined by the expressions (1) and (2) on the assumption that a slight gap exists between the valve sliding-contact surface 141a of the tubular seal member 131 and the outer peripheral surface of the peripheral wall portion 82 to allow sliding.

That is, as described above, the pressure of the cooling water in the housing 21 acts on the step surface 143 of the seal cylindrical member 131 as it is. On the other hand, the pressure of the cooling water in the housing 21 does not act on the valve sliding contact surface 141a as it is. Specifically, the pressure of the cooling water acts with a decrease in pressure when the cooling water flows through the minute gap between the valve sliding contact surface 141a and the peripheral wall portion 82 from the outer end edge to the inner end edge in the port radial direction. At this time, the pressure of the cooling water gradually decreases toward the inside in the port radial direction, and the seal cylindrical member 131 is pushed up toward the outside in the port axial direction.

As a result, the force obtained by multiplying the area S1 of the stepped surface 143 by the pressure P in the housing 21 acts on the stepped surface 143 of the tubular 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 housing 21 and the pressure reduction constant k acts on the valve sliding contact surface 141a of the seal cylindrical member 131.

As is clear from the equation (1), the areas S1 and S2 of the control valve 8 of the present embodiment are set so that k × S2 ≦ S1 is satisfied. Therefore, the relationship of P × k × S2 ≦ P × S1 holds.

Therefore, the force F1(F1 ═ P × S1) in the pressing direction acting on the stepped surface 143 of the tubular seal member 131 becomes greater than or equal to the force F2(F2 ═ P × k × S2) in the floating direction acting on the valve sliding contact surface 141a of the tubular seal member 131. Therefore, in the control valve 8 of the present embodiment, the space between the seal cylindrical member 131 and the peripheral wall portion 82 can be sealed only by the pressure of the cooling water in the housing 21.

On the other hand, in the present 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 141 a. Therefore, even if the pressure of the cooling water in the housing 21 increases, the valve sliding contact surface 141a of the seal cylindrical member 131 is suppressed from being pressed against the peripheral wall portion 82 by an excessive force. Therefore, in the case of using the control valve 8 of the present embodiment, it is possible to prevent the drive unit 23 for rotationally driving the valve body 22 from being increased in size and output, and to suppress premature wear of the seal cylinder member 131 and the respective bushes 78 and 84 (see fig. 4).

In this way, in the present embodiment, the area S2 of the valve sliding contact surface 141a is set to be larger than the area S1 of the step surface 143 in the range where the pressing force acting on the inner side of the tubular seal member 131 in the port axial direction is not lower than the floating force acting on the outer side of the tubular seal member 131 in the port axial direction. Therefore, the space between the sealing cylindrical member 131 and the peripheral wall 82 can be sealed while suppressing the excessive pressing force of the sealing cylindrical member 131 against the peripheral wall 82.

The holder 134 is configured to be movable in the port axial direction relative to the warm-up port 56 and the warm-up joint 62 in the gap Q1. In addition, the retainer 134 is configured to be detachable from at least any one of the warm-up port 56 and the warm-up joint 62 in the port axial direction. The retainer 134 has a retainer cylinder portion 151, a retainer flange portion 152, and a restricting portion 153.

The holder cylinder portion 151 extends in the port axial direction. The retainer cylinder portion 151 is inserted into the seal gap Q2 from the outside in the port axial direction. The bottom of the seal ring 133 can abut against the inner end surface of the retainer cylinder 151 in the axial direction of the port. That is, the retainer cylinder portion 151 restricts the movement of the seal ring 133 outward in the port axial direction.

The retainer flange portion 152 is provided to protrude outward in the port radial direction from the outer end portion of the retainer cylinder portion 151 in the port axial direction. The retainer flange portion 152 is disposed in a gap Q1 between an outer end surface in the port axial direction of the seal cylinder portion 101 and an inner end surface in the port axial direction of the intermediate diameter portion 122. Movement of the retainer 134 to the inside in the port axial direction is restricted by the seal cylinder portion 101, and movement of the retainer 134 to the outside in the port axial direction is restricted by the intermediate diameter portion 122.

The restricting portion 153 is formed to protrude in a cylindrical shape from the inner peripheral portion of the holder cylinder portion 151 to the outside in the port axial direction. The restricting portion 153 restricts the movement of the urging member 132 in the port radial direction together with the holder cylindrical portion 151.

Details of sealing-barrel parts

Fig. 7 is a perspective view of the seal cylinder member 131 viewed from the side of the valve sliding surface 141 a. Fig. 8 is an end view of the seal cylinder member 131 when viewed from the valve sliding surface 141a side.

The tubular seal member 131 includes a 1 st tubular portion 142 and a 2 nd tubular portion 141 having an outer diameter larger than that of the 1 st tubular portion 142, and a valve sliding contact surface 141a that slidably contacts the outer peripheral surface of the peripheral wall portion 82 of the valve body 22 is provided at an axial end portion (other axial end portion) of the 2 nd tubular portion 141. A stepped surface 143 is provided between the outer peripheral surface of the 1 st cylindrical portion 142 and the outer peripheral surface of the 2 nd cylindrical portion 141. The 1 st cylindrical portion 142 is formed to have an inner diameter smaller than that of the 2 nd cylindrical portion 141. A stepped surface 44 is provided between the inner peripheral surface of the 1 st tube portion 142 and the inner peripheral surface of the 2 nd tube portion 141.

The projection height of the peripheral wall of the axial end portion (the end portion on the inside in the port axial direction) of the 2 nd cylindrical portion 141 in the direction going to the peripheral wall portion 82 of the valve body 22 changes continuously in the circumferential direction along the shape of the outer peripheral surface of the peripheral wall portion 82. That is, the projecting height of the peripheral wall at the axial end of the 2 nd cylindrical portion 141 is continuously changed so that the valve sliding contact surface 141a comes into surface contact with the outer peripheral surface of the peripheral wall portion 82 of the valve body 22. The axial end of the 2 nd cylindrical portion 141 has the lowest projection height in the outermost region with respect to the direction along the axis O1 (the rotation axis of the valve body 22), and has the highest projection height in the outermost region with respect to the direction orthogonal to the axis O1 (the direction along the rotation direction of the valve body 22). Further, reference character C1 in fig. 8 is a center line showing the center of the valve hole 96(95, 97) in the axis O1 direction of the valve body 22.

The tubular seal member 131 is provided with a small outer diameter portion 55 in which the length L from the axial center O3 to the outer peripheral surface of the tubular seal member 131 is shorter than other regions in two regions (two regions including a portion where the projecting height in the valve body 22 direction is the largest) in which the projecting height in the direction to the peripheral wall portion 82 of the valve body 22 (hereinafter referred to as "projecting height in the valve body 22 direction") is high in the peripheral wall of the 2 nd cylindrical portion 141.

The small outer diameter portion 55 is formed by a plane P1 (1 st plane) in which the end on the valve sliding contact surface 141a side has a linear shape substantially parallel to the rotation axis (axis O1) of the valve body 22. In the present embodiment, the plane P1 extends parallel to the axial center O3 of the seal cylindrical member 131.

In the present embodiment, the inner peripheral surface of the 2 nd cylindrical portion 141 is formed in a circular shape having a constant length from the axial center O3 in the entire circumferential direction, but a 2 nd plane P2 (see fig. 8) substantially parallel to the plane P1 (the 1 st plane) may be formed in a region of the inner peripheral surface of the 2 nd cylindrical portion 141 having a high projecting height in the valve body 22 direction so as to bulge inward in the radial direction. In this case, the width of the 2 nd cylindrical portion 141 in the radial direction can be set to a constant width in the circumferential range of the seal cylindrical member 131.

< method of operating control valve >

Next, the operation method of the control valve 8 will be described.

As shown in fig. 1, in the main flow path 10, the cooling water sent from the water pump 3 exchanges heat with the engine 2 and then flows toward the control valve 8. As shown in fig. 4, the coolant having passed through the engine 2 in the main flow path 10 flows into the connection flow path 92 in the housing 21 through the inlet 37 a.

Some of the coolant flowing into the connection flow path 92 flows into the EGR outlet 51. The cooling water flowing into the EGR outlet 51 is supplied into the EGR passage 14 through the EGR joint 52. The cooling water supplied into the EGR passage 14 is subjected to heat exchange between the cooling water and the EGR gas in the EGR cooler 7, and then returned to the main passage 10.

On the other hand, of the coolant flowing into the connecting flow path 92, the coolant that does not flow into the EGR outlet 51 flows into the 2 nd side flow passage 91 in the housing axial direction. The cooling water flowing into the flow path 91 is distributed to the respective outlet ports while flowing in the flow path 91 in the case axial direction. That is, the cooling water flowing into the flow passage 91 is distributed to the flow passages 11 to 13 through the outlet port communicating with the corresponding valve hole among the outlet ports.

In the control valve 8, the valve body 22 is rotated about the axis O1 in order to switch the communication mode between the valve hole and the outlet port. Then, the rotation of the valve body 22 is stopped at a position corresponding to a communication mode desired to be set, and the valve hole and the outlet port communicate with each other in the communication mode corresponding to the stop position of the valve body 22.

< effects of the embodiment >

As described above, in the control valve 8 of the present embodiment, the small outer diameter portion 55, which has a length from the axial center O3 of the seal cylindrical member 131 to the outer peripheral surface shorter than the other regions, is provided in the region of the peripheral wall of the axial end portion of the seal cylindrical member 131 where the projection height in the valve element 22 direction is high. Therefore, even if the hydraulic pressure in the housing 21 acts on the region of the outer peripheral surface of the axial end portion of the seal cylindrical member 131 having a high projection height in the valve body 22 direction when the seal cylindrical member 131 is not in communication with the valve hole of the valve body 22, a large moment starting from the region having a low projection height in the valve body 22 direction is less likely to act on the seal cylindrical member 131.

That is, in the control valve 8 of the present embodiment, since the distance from the pressure receiving surface (the small outer diameter portion 55) outside the region of the cylindrical seal member 131 having a high projection height in the valve body 22 direction to the start point of the moment (the region having a low projection height) is shortened, the moment acting on the other end portion of the cylindrical seal member 131 is reduced. Therefore, the deformation of the cylindrical seal member 131 due to the moment can be suppressed so that the region of the cylindrical seal member 131 having a low projection height in the valve body 22 direction floats from the peripheral wall 82 of the valve body 22. Therefore, when the control valve of the present embodiment is used, the sealing performance between the seal cylindrical member 131 and the valve body 22 can be improved.

In the control valve 8 of the present embodiment, the small outer diameter portion 55 on the outer periphery of the seal cylindrical member 131 is formed by the plane P1 (the 1 st plane), and the end portion of the plane P1 on the valve sliding contact surface 141a side is formed in a linear shape substantially parallel to the rotation axis (the axis O1) of the valve body 22. Therefore, when the region of the end of the seal cylindrical member 131 having a high projection height in the valve body 22 direction receives the hydraulic pressure of the cooling water in the housing 21, the end of the small outer diameter portion 55 (the plane P1) having a linear shape comes into line contact with the peripheral wall portion 82 of the valve body 22. Therefore, in the case of this configuration, the contact range of the valve body 22 with the peripheral wall portion 82 is increased as compared with the configuration in which the end portion of the small outer diameter portion 55 is in point contact, and as a result, the end portion of the seal cylindrical member 131 is less likely to be worn.

Further, as described above, when the 2 nd plane P2 substantially parallel to the plane P1 (1 st plane) constituting the small outer diameter portion 55 is provided so as to bulge radially inward on the inner peripheral surface of the region of the tubular seal member 131 having a high projection height in the valve element 22 direction, the radial width of the valve sliding contact surface 141a of the tubular seal member 131 can be made uniform in the circumferential direction. That is, even if the plane P1 is provided on the outer peripheral side of the cylindrical seal member 131, the radial width of the valve sliding contact surface 141a of the cylindrical seal member 131 does not become narrower in a part of the circumferential direction. Therefore, in the case of the present configuration, local increase in the surface pressure due to decrease in the radial width of the valve sliding contact surface 141a can be suppressed, and thus wear of the valve sliding contact surface 141a in the region where the projection height in the valve body 22 direction is high can be suppressed.

In addition, when the above-described configuration is applied to the present embodiment, the 2 nd plane P2 is provided so as to bulge inward in the radial direction of the 2 nd tube portion 141 having a larger inner diameter than the 1 st tube portion 142. In this case, the cross section of the inner side of the 2 nd tube part 141 is narrowed by the bulge of the 2 nd plane P2, but the flow rate of the cooling water flowing out to the outlet is determined by the 1 st tube part 142 having a relatively small inner diameter, and therefore the 2 nd plane P2 does not affect the flow rate of the cooling water. Therefore, in this case, the flow rate of the cooling water flowing out to the outlet can be easily set and adjusted.

[ 2 nd embodiment ]

Fig. 9 is a perspective view of the tubular seal member 131A according to embodiment 2, viewed from the side of the valve sliding surface 141 Aa. Fig. 10 is an end view of the seal cylindrical member 131A when viewed from the valve sliding contact surface 141Aa side. Fig. 11 is a sectional view taken along line XI-XI of fig. 10, and fig. 12 is a sectional view taken along line XII-XII of fig. 10.

The tubular seal member 131A of the present embodiment has a 1 st tubular portion 142 and a 2 nd tubular portion 141A having an outer diameter larger than that of the 1 st tubular portion 142, similarly to the tubular seal member 131 of the 1 st embodiment. The 1 st cylinder 142 communicates with the outlet of the housing. Further, a valve sliding contact surface 141Aa that slidably abuts against the outer peripheral surface of the peripheral wall portion of the valve body is provided at an axial end portion (the other axial end portion) of the 2 nd cylindrical portion 141A. The protruding height of the valve sliding contact surface 141Aa is continuously changed 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 of the seal cylindrical member 142) is formed to be a constant width in the circumferential range of the seal cylindrical member 142.

The outer peripheral surface and the inner peripheral surface of the 1 st tube portion 142 are formed in a perfect circle shape, but the outer peripheral surface and the inner peripheral surface of the 2 nd tube portion 141A are formed in a substantially elliptical shape. More specifically, the outer peripheral surface and the inner peripheral surface of the 2 nd cylindrical portion 141A are formed in a substantially elliptical shape in which the region having the highest projection height in the valve body direction has a short diameter and the region having the lowest projection height in the valve body direction has a long diameter. In the present embodiment, the vicinity of the short diameter portion in the outer peripheral surface of the 2 nd cylindrical portion 141A is the small outer diameter portion 55A.

A stepped surface 143A is provided between the outer peripheral surface of the 1 st cylindrical portion 142 and the outer peripheral surface of the 2 nd cylindrical portion 141A, as in embodiment 1. However, since the outer peripheral surface of the 1 st cylindrical portion 142 is a perfect circle and the outer peripheral surface of the 2 nd cylindrical portion 141A is a substantially ellipse, the radial width of the stepped surface 143A varies in the circumferential direction by the difference between the shapes thereof.

A stepped surface 144A is provided between the inner peripheral surface of the 1 st tube portion 142 and the inner peripheral surface of the 2 nd tube portion 141A. The radial width of the inner peripheral stepped surface 144A is changed in the circumferential direction by the difference between the shape of the inner peripheral surface of the 1 st cylindrical portion 142 having a perfect circular shape and the shape of the 2 nd cylindrical portion 141A having a substantially elliptical shape, similarly to the outer peripheral stepped surface 143A. However, the stepped surface 144A is not present at a portion corresponding to a region where the other end portion of the seal cylindrical member 142 has the highest projecting height. That is, the inner peripheral surface of the region of the 2 nd cylindrical portion 141A having the highest projecting height is continuously formed without a step from the inner peripheral surface of the 1 st cylindrical portion 142.

In the tubular seal member 131A of the present embodiment, although the outer surface shape of the 2 nd cylindrical portion 141A is different, the small outer diameter portion 55A is provided in a region where the projecting height in the valve body direction is high in the peripheral wall of the axial end portion of the tubular seal member 131A as in the 1 st embodiment. Therefore, when the hydraulic pressure in the housing acts on the region with a high projection height on the short diameter side, a large moment starting from the region with a low projection height in the valve body direction is less likely to act on the seal cylindrical member 131A. Therefore, in the case of the present embodiment, the sealing performance between the seal cylindrical member 131A and the valve body can be improved.

In the tubular seal member 131A of the present embodiment, since the outer peripheral surface of the 2 nd tubular portion 141A is formed in a smooth, substantially elliptical shape, the 2 nd tubular portion 141A does not easily cause unnecessary turbulence in the flow of the cooling water in the housing when the control valve is actually used.

Further, in the tubular seal member 131A of the present embodiment, the circumferential range of the 2 nd cylindrical portion 141A is formed to a constant radial width, and therefore, local reduction in the contact surface pressure of the valve sliding contact surface 141Aa due to narrowing of the radial width in the vicinity of the small outer diameter portion 55A can be suppressed.

In the tubular seal member 131A according to the present embodiment, the inner peripheral surface of the region of the 2 nd cylindrical portion 141A having the highest projection height is continuously formed without a step from the inner peripheral surface of the 1 st cylindrical portion 142. Therefore, in the tubular seal member 131A according to the present embodiment, there is no stepped portion which becomes a bending start point between the inner peripheral surface of the region where the 2 nd tubular portion 141A has the highest projection height and the inner peripheral surface of the 1 st tubular portion 142. Therefore, in the case of the present embodiment, even if a large hydraulic pressure acts on the outer peripheral surface near the projecting end of the region of the 2 nd tube portion 141A where the projecting height is the highest, bending deformation is unlikely to occur between the 1 st tube portion 142 and the 2 nd tube portion 141A.

[ embodiment 3 ]

Fig. 10 is a perspective view of the cylindrical packing member 131B according to embodiment 3 as viewed from the side of the valve sliding surface 141Ba, and fig. 11 is an end view of the cylindrical packing member 131B as viewed from the side of the valve sliding surface 141 Ba.

The tubular seal member 131B of the present embodiment includes a 1 st tubular portion 142 and a 2 nd tubular portion 141B having a larger outer diameter than the 1 st tubular portion 142. The 1 st tubular portion 142 is the same as those of the 1 st and 2 nd embodiments, but the 2 nd tubular portion 141B has a shape different from those of the 1 st and 2 nd embodiments.

As in the other embodiments, the projecting height of the axial end of the 2 nd cylindrical portion 141B is continuously deformed along the outer surface shape of the peripheral wall portion of the valve body. The outer peripheral surface of the 2 nd cylindrical portion 141B is provided with a small outer diameter portion 55 having a length L from the axial center O3 of the seal cylindrical member 131B to the outer peripheral surface shorter than other regions in two regions having a high projection height in the valve body direction (two regions including a portion having the highest projection height in the valve body direction). Similarly to embodiment 1, the small outer diameter portion 55 is formed by a plane P1 (1 st plane) in which the end portion on the valve sliding contact surface 141Ba side has a linear shape substantially parallel to the rotation axis (axis O1) of the valve body. A 2 nd plane P2 substantially parallel to the plane P1 (1 st plane) is provided in a radially inward bulge in a region of the inner peripheral surface of the 2 nd cylindrical portion 141B where the projection height in the valve body direction is high.

In addition, the thick portion 60 is provided in two regions of the 2 nd cylinder portion 141B where the projection height in the valve body direction is low (two regions including a portion where the projection height in the valve body direction is the lowest). Each thick portion 60 is provided on the inner circumferential portion of the 2 nd cylindrical portion 141B so as to bulge radially inward. As shown in fig. 11, the thick portions 60 disposed at two positions are formed so as to be parallel to each other when the seal cylindrical member 131B is viewed in the axial direction (port axial direction). Radially inward of the 2 nd cylindrical portion 141B, linear inner edge portions facing each other are formed by the thick portion 60. In the case of the present embodiment, the thickest part of the thick portion 60 is disposed at the portion where the projecting height of the end portion of the 2 nd tube portion 141B is the lowest.

In the cylindrical seal member 131B of the present embodiment, as in the other embodiments described above, the small outer diameter portion 55 is provided in a region of the peripheral wall at the end in the axial direction of the cylindrical seal member 131B where the projection height in the valve body direction is high. Therefore, when the hydraulic pressure in the housing acts on the region with a high projection height, a large moment starting from the region with a low projection height in the valve body direction is less likely to act on the seal cylindrical member 131B. Therefore, in the case of the present embodiment, the sealing performance between the seal cylindrical member 131B and the valve body can be improved.

In the tubular seal member 131B according to the present embodiment, the 2 nd plane P2 substantially parallel to the plane P1 (the 1 st plane) constituting the small outer diameter portion 55 is provided on the inner peripheral surface of the region of the 2 nd cylindrical portion 141B having a high projection height in the valve body direction so as to bulge radially inward, and therefore, the radial width reduction of the region of the 2 nd cylindrical portion 141B having a high projection height can be suppressed. Therefore, the wear of the valve sliding contact surface 141Ba in the region where the projecting height of the 2 nd cylindrical portion 141B is high can be suppressed.

In addition, in the tubular seal member 131B according to the present embodiment, the thick portion 60 having a larger radial width than the other region in the circumferential direction of the 2 nd cylindrical portion 141B is provided in two regions having a low projecting height in the valve body direction of the 2 nd cylindrical portion 141B. Therefore, the radial width of the valve sliding contact surface 14Aa in the region where the projecting height of the 2 nd cylindrical portion 141B is low is increased. Therefore, it is possible to suppress an increase in the surface pressure in a region where the hertzian surface pressure is most likely to increase (a region where the projection height is low) when the seal cylindrical member 131B is pressed against the peripheral wall of the valve body. Therefore, when the tubular seal member 131B according to the present embodiment is used, premature wear of the portion of the 2 nd cylindrical portion 141B having a low projection height can be suppressed.

The present invention is not limited to the above-described embodiments, and various design changes can be made without departing from the scope of the invention.

Description of the reference numerals

8 control valve

21 outer cover

22 valve body

37a inflow port

41b radiator outflow (outflow)

50 linear inner edge part

55. 55A small outer diameter part

56a warm air outflow port (outflow port)

66a air conditioner outlet (outflow)

82 peripheral wall part

95. 96, 97 valve hole

131. 131A, 131B seal cartridge parts

141. 141A, 141B No. 2 cylinder part

141a, 141Aa, 141Ba valve sliding contact surface

142 the 1 st cylinder part

O2 axle center

P1 plane (1 st plane)

P2 plane 2.

Claims (8)

1. A control valve is provided with:

a housing having an inlet through which liquid flows from outside and an outlet through which the liquid flowing into the housing flows out to outside;

a valve body which is rotatably disposed in the housing and has a peripheral wall portion in which a valve hole for communicating the inside and the outside is formed; and

a seal cylinder member having one axial end portion communicating with the outlet port and the other axial end portion provided with a valve sliding contact surface slidably abutting against an outer peripheral surface of the peripheral wall portion at a position overlapping at least a part of a rotation path of the valve hole of the valve body,

a projection height of the other end portion of the seal cylinder member in the axial direction in the direction to the peripheral wall portion changes continuously in the circumferential direction along a shape of an outer peripheral surface of the peripheral wall portion,

the above-mentioned control valve is characterized in that,

in the region of the other end of the seal cylindrical member where the projection height is high, a small outer diameter portion is provided, the length from the axial center of the seal cylindrical member to the outer peripheral surface of the seal cylindrical member being shorter than the other region.

2. The control valve of claim 1,

the small outer diameter portion is formed by a 1 st plane having a linear shape substantially parallel to the rotation axis of the valve body at an end portion on the valve sliding contact surface side.

3. The control valve of claim 2,

a 2 nd plane substantially parallel to the 1 st plane is formed on an inner peripheral surface of a region of the other end portion of the tubular seal member having a high projecting height so as to project radially inward of the tubular seal member.

4. The control valve of claim 3,

the seal tube member includes:

a 1 st cylinder part located on the one end side and communicating with the outlet port; and

a 2 nd cylinder part located on the other end side, an axial end face of which constitutes the valve sliding contact surface and an inner peripheral surface of which is formed with the 2 nd plane so as to bulge out,

the inner diameter of the 1 st cylindrical portion is formed smaller than the inner diameter of the 2 nd cylindrical portion.

5. The control valve of claim 1,

the outer peripheral surface of the other end portion of the seal cylinder member is formed in a substantially elliptical shape having a short diameter in a region having the highest projection height and a long diameter in a region having the lowest projection height.

6. The control valve of claim 5,

the radial width of the other end portion of the seal cylindrical member is formed to be a constant width in the circumferential range of the seal cylindrical member.

7. The control valve according to claim 5 or 6,

the seal tube member includes:

a 1 st cylinder part located on the one end side and communicating with the outlet port; and

a 2 nd cylindrical portion located on the other end portion side, an axial end surface of which constitutes the valve sliding contact surface,

the outer peripheral surface and the inner peripheral surface of the 2 nd cylindrical part are formed in a substantially elliptical shape in which a region having the highest projection height is a short diameter and a region having the lowest projection height is a long diameter,

an inner peripheral surface of a region of the 2 nd cylindrical portion where the projecting height is the highest is continuously formed without a step from an inner peripheral surface of the 1 st cylindrical portion.

8. The control valve according to any one of claims 1 to 7,

the width in the radial direction of the region having the lower projecting height of the other end portion is formed to be wider than the width in the radial direction of the region having the higher projecting height of the other end portion.

Images