WO2016067463A1

WO2016067463A1 - Fluid control valve

Info

Publication number: WO2016067463A1
Application number: PCT/JP2014/079102
Authority: WO
Inventors: 克典高井; 直樹井花
Original assignee: 三菱電機株式会社
Priority date: 2014-10-31
Filing date: 2014-10-31
Publication date: 2016-05-06
Also published as: JPWO2016067463A1; JP6230723B2

Abstract

A seal member 40 is provided not between a connecting surface 21b and a connecting surface 31b, which come into contact with each other when an actuator-side housing 21 and a valve-side housing 31 are fastened by means of a bolt 22, but is provided in a space B formed by having a facing surface 21A and a facing surface 31A separated from each other. The seal member 40 seals between the facing surface 21A and the facing surface 31A by being in contact with the facing surface 21A and the facing surface 31A.

Description

Fluid control valve

This invention relates to a fluid control valve installed in a conduit through which a fluid flows, and more particularly to a structure for preventing fluid leaking from around a valve shaft from flowing out.

For example, in an exhaust gas recirculation (EGR) valve described in Patent Document 1, a valve-side housing having a fluid passage through which exhaust gas flows and an actuator-side housing having an actuator section that drives the valve are screwed. They are connected using members.
A seal member is sandwiched between the valve side housing and the actuator side housing at the part fastened with the screw member so that the exhaust gas does not flow out from the connecting portion between the valve side housing and the actuator side housing. It is in the state.

JP 2004-301086 A

When the seal member is sandwiched between the parts fastened by the screw member as described above, when the temperature changes in the use environment, the linear expansion coefficients of the screw member, the two connected housings, and the seal member are respectively Due to the difference, the fastening force of the screw member may be reduced. Such a decrease in the fastening force of the screw member becomes more conspicuous as the temperature increases (for example, about 700 ° C. to 800 ° C.). And it is also conceivable that the fastening can be removed when external vibration is applied in a state where the fastening force is reduced due to the temperature change.

The present invention has been made to solve the above-described problems, and is capable of preventing a fluid leaking from around the valve shaft from flowing out while suppressing a decrease in fastening force due to a temperature change. The purpose is to obtain a control valve.

The fluid control valve according to the present invention includes a first housing having a fluid passage that is opened and closed by the valve, a second housing that is fastened with the opposing surfaces of the first housing spaced apart from each other, and a second housing And is inserted into a through-hole penetrating the actuator portion that generates the driving force and the facing surface of the first housing and the facing surface of the second housing, and opens and closes the valve in response to the driving force of the actuator portion. A sealing member that is provided between the opposing surface of the first housing and the opposing surface of the second housing and seals between the opposing surfaces by contacting both opposing surfaces. It is characterized by having.

According to the present invention, it is possible to obtain a fluid control valve that prevents a fluid leaking from around the valve shaft from flowing out while suppressing a decrease in fastening force due to a temperature change.

It is a figure which shows the fluid control valve which concerns on Embodiment 1 of this invention. It is a cross-sectional enlarged view of A part of FIG. It is a figure which shows the valve side housing. It is a perspective view which shows a sealing member. It is the figure which expanded a part of FIG.

Hereinafter, in order to explain the present invention in more detail, modes for carrying out the present invention will be described with reference to the accompanying drawings.
Embodiment 1 FIG.
FIG. 1 is a diagram showing a fluid control valve according to Embodiment 1 of the present invention, in which the fluid control valve according to Embodiment 1 is embodied as an EGR valve that circulates engine exhaust gas into an intake passage. Show. The EGR valve shown in FIG. 1 is a butterfly valve, and the valve 33 rotates integrally with the valve shaft 32 to open and close the exhaust gas passage (fluid passage) 34. The configuration includes an actuator unit 10, a driving force transmission unit 20, and a valve unit 30.

The actuator unit 10 includes a motor 11 and generates a rotational driving force for opening and closing the valve 33. The output shaft of the motor 11 is attached to a gear mechanism disposed inside the driving force transmission unit 20.

The driving force transmission unit 20 includes the gear mechanism and an actuator-side housing 21 that accommodates the gear mechanism. The output shaft of the motor 11 and the valve shaft 32 are connected via this gear mechanism, and the rotational driving force of the motor 11 is transmitted to the valve shaft 32 via the gear mechanism.
For example, a pinion gear attached to the output shaft of the motor 11 and the valve shaft 32 are engaged with each other by a gear, and the rotational driving force of the motor 11 is directly transmitted to the valve shaft 32.
The actuator side housing 21 embodies the second housing of the present invention, and is made of, for example, aluminum. The actuator side housing 21 is attached to the actuator side housing 21 as shown in FIG.

The valve unit 30 is connected to a conduit through which exhaust gas flows, and controls the flow rate of exhaust gas by opening and closing the valve 33. The valve-side housing 31 that constitutes the valve portion 30 embodies the first housing according to the present invention, is made of heat-resistant steel such as cast iron or stainless steel, and has an exhaust gas passage 34 provided therein.

The valve-side housing 31 is formed with a through hole 31a that connects the outside of the housing and the exhaust gas passage 34, and the valve shaft 32 is inserted into the through hole 31a. The valve 33 rotates integrally with the valve shaft 32 to open and close the exhaust gas passage 34.
The actuator side housing 21 and the valve side housing 31 are fastened by a bolt 22 that is a screw member.

FIG. 2 is an enlarged cross-sectional view of a portion A in FIG. 1, and shows a cross section of the portion A cut in the axial direction. FIG. 3 is a view showing the valve-side housing 31, and shows a configuration viewed from the side facing the actuator-side housing 21.

The actuator side housing 21 is formed with a through hole 21a that extends to the valve portion 30 side, and the valve shaft 32 is inserted into the through hole 21a. As shown in FIG. 2, the

opposing surfaces

21A and 31A are spaced apart to form a space B, and the actuator-side housing 21 is connected to the valve-side housing 31 only through the connection surface 21b. The connection surface 21b protrudes toward the valve portion 30 from the facing surface 21A that faces the valve-side housing 31 with the space B interposed therebetween. The connection surface 21b is located on the outer periphery of the facing surface 21A. Moreover, the bolt hole 21c which inserts the volt | bolt 22 is formed through the connection surface 21b. The through hole 21a penetrates the facing surface 21A.

As shown in FIG. 2, the actuator side housing 21 is formed with a cooling passage 23 for circulating cooling water. By providing the cooling passage 23, the heat of the exhaust gas passing through the valve unit 30 is suppressed from being transmitted to the actuator unit 10.
The space B also suppresses the heat of the exhaust gas passing through the valve portion 30 from being transmitted from the valve side housing 31 to the actuator side housing 21.

The valve-side housing 31 has a hole communicating with the through hole 31a, and the bearing 35 is mounted in the hole. The hole is formed so as to penetrate the facing surface 31 </ b> A to the actuator-side housing 21. The valve shaft 32 inserted into the through hole 31 a is rotatably supported by the inner peripheral surface of the bearing portion 35.
The facing surface 31A is opposed to the facing surface 21A with the space B interposed therebetween. The connection surface 31b is a connection surface that contacts the connection surface 21b of the actuator-side housing 21, and is located on the outer periphery of the facing surface 31A. The connection surface 31b passes through a bolt hole 31c formed coaxially with the bolt hole 21c.
On the facing surface 31A, the periphery of the hole portion in which the bearing portion 35 is mounted is raised, and a step portion 31d having an upper surface that is substantially rectangular is formed.

Incidentally, a slight gap is formed between the inner peripheral surface of the bearing portion 35 that rotatably supports the valve shaft 32 and the outer peripheral surface of the valve shaft 32. For this reason, the exhaust gas flowing through the exhaust gas passage 34 reaches the space B through this gap, and shaft leakage occurs. FIG. 2 shows an exhaust gas flow F at the time of shaft leakage. In this way, the space B is sealed with, for example, stainless steel so that the exhaust gas leaking from the periphery of the valve shaft 32 does not pass between the connection surface 21b and the connection surface 31b and flow out of the EGR valve. A member 40 is provided.

FIG. 4 is a perspective view of the seal member 40. The seal member 40 formed along the outer shape of the upper surface of the stepped portion 31d is a substantially rectangular frame-like member, and has a C-shaped cross section. The curved portion of the C-shaped cross section is a curved portion 41, and the upper and lower straight portions are

flat portions

42 and 43. The curved portion 41 is convex toward the inside of the frame-shaped seal member 40, and the

flat portions

42 and 43 are extended from both ends of the curved portion 41 toward the outside of the frame-shaped seal member 40. Yes. The curved portion 41 and the

flat portions

42 and 43 that are integrally formed have an elastic shape that has a function of elastically deforming and pushing back in a direction opposite to the external force when an external force is applied in a direction in which the interval between the

flat portions

42 and 43 is reduced. It functions as a so-called leaf spring.
The flat part 43 is provided with a positioning piece (positioning part) 44 extending in a direction away from the flat part 42. In the example of FIG. 4, one positioning piece 44 is provided at each side position of the substantially rectangular sealing member 40, and a total of four positioning pieces 44 are formed.

FIG. 5 is an enlarged view of the vicinity of the seal member 40 in FIG. The seal member 40 is placed on a step portion 31d formed on the facing surface 31A of the valve-side housing 31, the flat portion 42 contacts the facing surface 21A of the actuator-side housing 21, and the flat portion 43 is formed on the valve-side housing. 31 is in contact with the opposing surface 31A. In this way, the

flat portions

42 and 43 that contact the facing

surfaces

21A and 31A and the curved portions 41 that are formed integrally with the

flat portions

42 and 43 constitute a contact portion. Further, the positioning piece 44 comes into contact with the side surface of the stepped portion 31d to restrict the movement in the direction perpendicular to the valve shaft 32, and positioning on the facing surface 31A is performed. Thus, the seal member 40 seals between the facing surface 21A and the facing surface 31A, and prevents the exhaust gas leaking from the periphery of the valve shaft 32 from flowing out.

On the other hand, conventionally, the valve shaft 32 is configured by surrounding the stepped portion 31d with a gasket as a seal member between the connection surface 21b and the connection surface 31b without providing the seal member 40. The exhaust gas leaked from the surroundings was prevented from flowing outside. When configured in this manner, the fastening force of the bolt 22 is reduced due to the difference in the linear expansion coefficients of the bolt 22, the actuator side housing 21, the valve side housing 31, and the gasket. That is, the gasket has an effect that the fastening force is reduced when the bolt 22 is fastened. Furthermore, in an EGR valve that is exposed to a high temperature environment, a gasket made of mica, clayey material, or the like is used. The linear expansion coefficient of such a material is the same as that of aluminum constituting the actuator side housing 21 and valve side housing 31. It differs greatly from the linear expansion coefficient of the cast iron. Therefore, the fastening force of the bolt 22 is greatly reduced by sandwiching the gasket between the connection surface 21b and the connection surface 31b.

In the present invention, the sealing member 40 is installed in the space B formed by separating the facing surface 21A and the facing surface 31A, instead of being sandwiched between the connecting surface 21b and the connecting surface 31b. For this reason, the influence which the sealing member 40 has with respect to the fastening with the volt | bolt 22 can be reduced, and the fall of the fastening force of the volt | bolt 22 resulting from a temperature change can be suppressed.

Further, the seal member 40 is configured as a leaf spring, and due to its elasticity, the flat portion 42 is pressed against the facing surface 21A of the actuator side housing 21 and the flat portion 43 is pressed against the facing surface 31A of the valve side housing 31. Yes. Therefore, even if the gap between the opposing surface 21A and the opposing surface 31A changes due to a temperature change, the contact state with the opposing

surfaces

21A and 31A can be maintained following the change.

The heat of exhaust gas passing through the valve portion 30 is transmitted to the actuator-side housing 21 and the actuator portion 10 through the seal member 40 because the seal member 40 is in contact with the opposing

surfaces

21A and 31A. Therefore, in order to suppress this heat transfer, it is desirable that the seal member 40 is made of a material having low thermal conductivity. For example, a material having lower thermal conductivity than aluminum constituting the actuator-side housing 21, specifically, stainless steel already described may be used, or mica, carbon, or the like may be used. Further, heat transfer to the actuator-side housing 21 can be suppressed by making the plate thickness of the seal member 40 thinner than the gap between the facing surface 21A and the facing surface 31A. The plate thickness of the seal member 40 is reduced to, for example, about 0.2 mm or less.

Moreover, the sealing member 40 should just be an elastic shape which press-contacts to opposing

surface

21A, 31A, and is not restricted to the shape shown in figure. For example, the curved portion 41 may be configured to be convex outward rather than configured to be convex toward the inside of the frame-shaped seal member 40.
In the above description, a total of four positioning pieces 44 are partially provided. However, as a positioning wall extending from the entire circumference of the frame of the seal member 40, the circumference of the side surface of the step portion 31d is surrounded. You may form in.

In the above description, the step portion 31d is formed on the facing surface 31A, and the seal member 40 is placed on the step portion 31d. However, the facing surface 31A may be flattened and a stepped portion may be formed on the facing surface 21A, and the sealing member 40 may be placed on the stepped portion and the positioning piece 44 may be positioned on the facing surface 21A.

Moreover, in the above, the structure which the connection surface 21b and the connection surface 31b contact directly was shown. However, in order to suppress the heat of the exhaust gas from being transmitted from the connection surface 31b to the connection surface 21b, a plate having low thermal conductivity is sandwiched between the connection surface 21b and the connection surface 31b, and the connection surface 21b and the connection surface It is good also as a structure which 31b contacts indirectly. In this case, it is necessary to consider that the fastening force of the bolt 22 is not further reduced by the plate sandwiched between the connection surface 21b and the connection surface 31b. Therefore, the plate is made of a material having a low thermal conductivity and a linear expansion coefficient that is not significantly different from that of the actuator-side housing 21 and the valve-side housing 31, for example, stainless steel.

In the above description, the fluid control valve is used as the EGR valve. However, the fluid control valve may be used as a valve other than the EGR valve.
In the above description, the butterfly type fluid control valve has been described, but a poppet type, flap type, or other fluid control valve may be used.

As described above, according to the fluid control valve according to the first embodiment, the seal member 40 has the connection surface 21b and the connection surface 31b that come into contact when the actuator-side housing 21 and the valve-side housing 31 are fastened with the bolts 22. The opposed surface 21 </ b> A and the opposed surface 31 </ b> A are provided in a space B formed apart from each other. Accordingly, it is possible to prevent the exhaust gas leaking from the periphery of the valve shaft 32 from flowing out to the outside while suppressing a decrease in the fastening force of the bolt 22 due to the temperature change.

Further, the seal member 40 is provided with a positioning piece 44 for positioning the mounting position on the facing

surfaces

21A and 31A. Therefore, the seal member 40 is easily positioned.

Further, in the sealing member 40, the contact portions that contact the opposing

surfaces

21A and 31A have an elastic shape, and the contact portions are in pressure contact with the opposing

surfaces

21A and 31A, respectively. Therefore, the seal member 40 can maintain a contact state with the opposing

surfaces

21A and 31A, and can always seal between the opposing surface 21A and the opposing surface 31A.

The seal member 40 is made of a material having a lower thermal conductivity than the actuator-side housing 21 and a thickness thinner than the gap between the facing surface 21A and the facing surface 31A. Therefore, the heat of the fluid flowing through the valve side housing 31 can be prevented from being transmitted to the actuator unit 10 via the seal member 40.

In addition, by using the fluid control valve according to the first embodiment as an EGR valve, even if the exhaust gas to be circulated is at a high temperature, the exhaust gas is prevented from flowing out while suppressing a decrease in fastening force. can do.

In the present invention, any component of the embodiment can be modified or any component of the embodiment can be omitted within the scope of the invention.

As described above, in the fluid control valve according to the present invention, even when exposed to a high temperature environment, the fluid leaking from the periphery of the valve shaft flows out to the outside while suppressing a decrease in the fastening force of the bolt due to the temperature change. For example, it is suitable for use as an EGR valve through which high-temperature exhaust gas flows.

10 actuator section, 11 motor, 20 driving force transmission section, 21 actuator side housing (second housing), 21A facing surface, 21a through hole, 21b connection surface, 21c bolt hole, 22 bolt, 23 cooling passage, 30 valve section , 31 Valve side housing (first housing), 31A facing surface, 31a through hole, 31b connection surface, 31c bolt hole, 31d step, 32 valve shaft, 33 valve, 34 exhaust gas passage (fluid passage), 35 bearing Part, 40 sealing member, 41 curved part, 42, 43 flat part, 44 positioning piece (positioning part).

Claims

A first housing having a fluid passage opened and closed by a valve;
A second housing fastened to the first housing with the opposing surfaces spaced apart from each other;
An actuator unit attached to the second housing and generating a driving force;
A fluid provided with a valve shaft that is inserted into a through-hole penetrating the opposing surface of the first housing and the opposing surface of the second housing, and that opens and closes the valve by receiving the driving force of the actuator unit. In the control valve,
A seal member is provided between the facing surface of the first housing and the facing surface of the second housing, and seals between the facing surfaces by contacting both of the facing surfaces. Fluid control valve.
The fluid control valve according to claim 1, wherein the seal member includes a positioning portion for positioning an attachment position on the facing surface.
The seal member has an elastic shape at a contact portion that contacts both the opposed surfaces,
The fluid control valve according to claim 1, wherein the contact portion is in pressure contact with both of the opposing surfaces.
The fluid control valve according to claim 1, wherein the seal member is made of a material having a lower thermal conductivity than the second housing and a thickness thinner than a gap between the opposing surfaces.
The fluid control valve according to claim 1, wherein the fluid control valve is an exhaust gas recirculation valve.