WO1995022023A1

WO1995022023A1 - Flow rate control rotary valve

Info

Publication number: WO1995022023A1
Application number: PCT/JP1995/000157
Authority: WO
Inventors: Shinji Sugihara; Akira Furukawa
Original assignee: Nippondenso Co., Ltd.
Priority date: 1994-02-10
Filing date: 1995-02-07
Publication date: 1995-08-17

Abstract

An inner circumferential surface of a housing (1) rotatably supports a rotary shaft (4) via a pair of bearings (3), and a valve disc (5) fixed to the rotary shaft (4) controls the opening of at least one of inlet hole (19) and outlet hole (14) both made open in the inner circumferential surface. A biassing means (25) biasses the two bearings (3) towards one of the two holes. Therefore, the valve disc (5) is displaced toward or pressed against an inner circumferential surface of a collar (2) by the biassing means (25) via the two bearings (3), whereby it is possible to reduce leakage that would take place when the valve is closed. Due to this, even if a combination of the housing (1) and valve disc (5) which have a large linear expansion coefficient difference is selected, it is still possible to reduce leakage, this increasing the degree of freedom in selection of combination of raw materials. In addition, even if there is a large difference in linear expansion coefficient between the housing (1) and the bearings (3), there is no risk of the bearings (3) being loosened due to the expansion of the collar (2), and therefore it is possible to select various types of materials such as resin as a material for the housing.

Description

Description Flow control rotary valve Technical field

The present invention relates to a flow control rotary valve, and is preferably used as an intake air flow control valve for an internal combustion engine.

Background art

A housing having a valve chamber with an inflow hole and an outflow hole opened at the axial center of the inner peripheral surface, and rotatably supported by a pair of bearings fitted to both ends of the inner peripheral surface. 2. Description of the Related Art There is known a flow control valve having a rotating shaft that is fixed to a rotating shaft and a valve body that is housed in a valve chamber and that adjusts an opening of one of both holes by rotating. (For example, Japanese Patent Application Laid-Open No. 59-15939).

However, the above-described conventional flow control rotary valve has the following problems.

First, due to the difference in linear expansion coefficient between the housing and the bearing, the relative position between the housing and the bearing is shifted, and the clearance between the inner peripheral surface of the housing and the valve body is reduced. There was a problem that the arrangement became large and the leakage became large.

On the other hand, in order to reduce the difference in the linear expansion coefficient between the housing and the valve body, the range of choice of materials was reduced, which caused problems in terms of cost, manufacturing process, durability, and the like. For example, when both are made of metal, there is a problem of weight increase compared to when both are made of resin, and when both are made of resin, the valve body is made of resin compared to when both are made of metal. Therefore, there is a problem that the strength is weak. For this purpose, it is preferable that the housing is formed of resin (for example, nylon) and the valve body is made of metal (for example, aluminum alloy or stainless steel). As a result, for the reasons described above, The inflation of the housing increases the clearance between the housing and the valve body, and further increases leakage.

Accordingly, an object of the present invention is to provide a flow control rotary valve capable of reducing leakage caused by a difference in linear expansion coefficient between a housing, a bearing, or a valve body. And It is another object of the present invention to provide a flow control rotary valve capable of reducing leakage without requiring improvement in manufacturing accuracy. Disclosure of the invention

In order to achieve the above object, according to the first aspect, a frame body having a valve chamber having an inlet hole and an outlet hole opened at an axially central portion of an inner peripheral surface, and fitted to both ends of the inner peripheral surface. A flow control comprising: a rotating shaft rotatably supported by a pair of bearings; and a valve body fixed to the rotating shaft and housed in the valve chamber and adjusting the opening of the hole by rotation. A rotary valve,

By providing an urging means for urging the bearing on one side of the inner peripheral surface of the frame, a clearance between the valve element and the inner peripheral surface of the frame due to thermal expansion is provided. The configuration is characterized by minimizing the change in the size.

According to this configuration, the inner peripheral surface of the housing rotatably supports the rotating shaft via the pair of bearings, and the valve body fixed to the rotating shaft is opened to the inner peripheral surface. At least one of the inflow hole and the outflow hole is controlled in opening. The biasing means biases both bearings toward one of the two holes.

Therefore, the valve body is displaced or pressed toward the hole by the urging means through the two bearings, whereby leakage at the time of closing the valve can be reduced. For this reason, even if a combination having a large difference in the linear expansion coefficient between the housing and the valve body is selected, the leakage can be reduced, and the degree of freedom of the material selection combination increases.

In addition, even if there is a large difference in the coefficient of linear expansion between the housing and the bearing, the bearing will not loosen, and various materials such as resin are selected as the housing material. can do.

Furthermore, cleanliness management between the inner peripheral surface of the housing and the valve body is possible. This makes it easier to reduce leakage without improving manufacturing accuracy.

According to a second aspect of the present invention, in addition to the configuration of the first aspect, a plurality of the outflow holes are provided, and the urging means has a cross-sectional area of the outflow hole which is the most. A configuration is adopted in which the bearing is urged toward the peripheral surface of the inside of the frame in which a large outflow hole is formed.

In the third invention, a resin housing having a valve chamber having an inflow hole and an outflow hole opened at an axially central portion of an inner peripheral surface, and the valve chamber having openings at positions corresponding to the both holes. And a metal collar having a pair of bearings fitted at both ends thereof, and a turn supported rotatably by the pair of bearings, while being in close contact with the inner peripheral surface of the housing. A flow control rotary valve comprising: a dynamic shaft; and a valve body fixed to the rotary shaft, housed in the valve chamber, and adjusting an opening degree of the hole by rotation.

By providing a biasing means for biasing the bearing on one side of the inner circumferential surface of the collar, a change in the clearance between the valve body and the inner circumferential surface of the collar due to thermal expansion is reduced. A configuration characterized by this is adopted.

According to this configuration, it is easy to form and dispose the urging means, and a clearance is generated between the color fitted to the bearing and the inner peripheral surface of the housing. In addition, leakage from the gap between the valve body and the color can be significantly reduced.

According to a fourth aspect of the present invention, in addition to the configuration of the third aspect, the biasing means is located at a fitting portion of the pair of bearings to bias the pair of bearings, and is provided integrally with the collar. The configuration is characterized by the elastic projections provided.

With this configuration, even if the clearance due to the difference in linear expansion coefficient is mainly formed between the outer peripheral surface of the collar and the inner peripheral surface of the housing, the bias to the bearing causes By preventing an increase in leakage from the gap between the valve element and the color, and by providing an elastic projection integrally with the color, the number of parts can be reduced. According to a fifth aspect of the present invention, in addition to the configuration of the fourth aspect, the color has a cylindrical shape in which a pair of ends are opposed to each other with a gap therebetween. A configuration characterized by being elastically deformed and closely contacting the inner peripheral surface of the housing is employed.

According to this configuration, even if a clearance occurs between the housing and the color, the color spreads to the outer peripheral side, thereby preventing play between the color and the housing. It can be.

According to a sixth aspect of the present invention, in a flow control rotary valve for rotating a valve body by energizing a coil,

A resin housing having a valve chamber that houses the valve body and has an inflow hole and an outflow hole opened in the circumferential direction, and a coil chamber that houses the coil, and corresponds to both housing holes. An opening, and a pair of bearings provided at both ends, a metallic collar which is in close contact with an inner peripheral surface of the housing so as to cover a valve chamber of the housing;

A rotating shaft that is rotatably supported by the pair of bearings and has a valve body that is housed in the valve chamber and that adjusts an opening of the opening of the collar;

Urging means for urging the bearing against the inner peripheral surface of the collar to maintain a predetermined clearance between the valve body and the inner peripheral surface of the collar;

The configuration is characterized by having.

According to this configuration, since the housing is formed of resin, the coil chamber and the valve chamber can be formed in a body, and the weight can be reduced.

Furthermore, since the urging means urges the bearing, the clearance between the valve body and the inner peripheral surface of the collar can always be kept at a predetermined level, so that leakage can be reduced. You.

According to a seventh aspect of the present invention, in addition to the configuration of the sixth aspect, the urging means is provided on a color and is an elastically deformable projection. The configuration is characterized in that the bearing is biased toward the inner peripheral surface having the collar opening.

According to this configuration, since the biasing means is a projection provided on the collar, it can be formed integrally with the collar, thereby preventing leakage between the valve body and the inner peripheral surface of the collar without increasing the number of parts. , Easily possible.

According to an eighth aspect of the present invention, in addition to the configuration of the seventh aspect, the collar has a cylindrical shape in which a pair of ends are opposed to each other with a gap therebetween. The elastic member is elastically deformed so as to be in close contact with the inner peripheral surface of the housing.

According to this configuration, even if a clearance occurs between the housing and the collar, the collar extends to the outer peripheral side, thereby preventing play between the collar and the housing. It can be. BRIEF DESCRIPTION OF THE FIGURES

FIG. 1 is an axial cross-sectional view of the flow control rotary valve according to the first embodiment. FIG. 2 is an assembly diagram of a rotating portion of the flow control rotating valve and a color. Fig. 3 (a) is a developed view of the valve element. Fig. 3 (b) is a front view of the valve element. FIG. 4 is a front view of the stove. FIG. 5 is a front view of the flow control rotary valve. Figure 6 is an expanded view of the color. Figure 7 is a front view of the color. FIG. 8 is a circuit diagram of a drive circuit for driving the coil of the flow control rotary valve. FIG. 9 is a schematic explanatory view for explaining rotation of the flow control rotation valve. FIG. 10 is a schematic explanatory view for explaining rotation of the flow control rotation valve. FIG. 11 is a schematic explanatory diagram for explaining the rotation of the flow control rotation valve. FIG. 12 is a characteristic diagram showing the relationship between the duty ratio of the input voltage of the flow control rotary valve and the air flow rate. FIG. 13 is a characteristic diagram showing the relationship between the duty ratio of the input voltage of the flow control rotary valve and the air flow rate. BEST MODE FOR CARRYING OUT THE INVENTION

(Example 1)

Hereinafter, an air flow control valve according to an embodiment of the present invention will be described with reference to the drawings.

FIG. 1 shows an axial sectional sectional view of the air flow control valve of this embodiment. This air flow control valve has a housing 1 made of a resin molded body with glass powder mixed therein, and the housing 1 is a valve housing having a cylindrical valve housing space 10 with both ends open. It comprises a part 11 and a solenoid housing part 12 integrally formed at one axial end of the knob housing part 11. A collar 2 is adhered to the inner peripheral surface of the valve housing portion 11 facing the valve housing space 10, and a pair of ball bearings 3 is fitted into both ends of the color 2. These ball bearings 3 rotatably support a rotating shaft 4, and as described later, a valve element 5 is located between the pair of ball bearings 3 and is fixed to the rotating shaft 4. Reference numeral 13 denotes a plate which is inserted into the right end opening 11a of the knob housing part 11 and closes it. A cylindrical valve chamber 100 is defined by the inner peripheral surface of the collar 2 and the end surface of the two spherical shaft bearings 3.

External air inflows through the valve chamber 100 through an inflow port 19a, which will be described later, which is opened in the collar 12, and an inflow port 19, which will be described later, which is opened in the peripheral wall of the valve housing portion 11. Through the outflow port 14a opened in the color 2 and the main outflow hole 14 opened in the peripheral wall of the valve housing part 11, communicating with the outside air outflow space, Similarly, it communicates with an outflow pipe (not shown) through an outflow port 15a opened in the collar 2 and a sub outflow hole 15 opened in the peripheral wall of the valve housing portion 11. As will be described later, the opening degree of the outflow holes 14 and 15 is controlled by the rotation of the valve element 5, and the flow rate is thereby controlled.

The cross-sectional area of the main outlet 14 is set to be larger than the cross-sectional area of the sub outlet 15.

The solenoid housing 12 is located adjacent to the valve accommodation space 10 A cylindrical magnet rotor accommodating space 16 formed at both ends and coaxial with the chamber 100, and a right angle formed without intersecting with the magnet rotor accommodating space 16 adjacent to the upper portion of the magnet rotor accommodating space 16. And a coil housing space 17 having a cylindrical shape with both ends open. The coil portion 61 of the rotary solenoid (rotary actuator) 6 shown in FIG. 5 is fitted into the coil accommodating space 17, and the magnet rotor accommodating space 16 is fitted into the magnet rotor accommodating space 16. The base 62 a of the yoke 62 of the mouthpiece solenoid 6 is accommodated.

A permanent magnet 6 3 is fitted and fixed to the left end of the rotating shaft 4. The permanent magnet 63 is inserted into the magnet rotor chamber 16, and has an opening 6 opened at the base 6 2 a of the yoke 6 2. It is rotatably housed in 2b. Numeral 65 denotes a plate which is inserted into the left end opening 16a of the magnet rotor storage space 16 and closes it.

FIG. 2 shows an axial sectional sectional view of a subassembly including the collar 2, the ball bearing 3, the rotating shaft 4, and the valve element 5.

As will be described later, the collar 2 is formed by bending a stainless steel thin plate into a cylindrical shape, and a valve body 5 is fixed in the collar 2 and a ball bearing 3 and a ring 46 are assembled. The driving shaft 4 is press-fitted, and then the other ball bearing 3 is press-fitted, and the sub-assembly is completed.

Figure 3 shows a development view of the valve element 5 before bending.

The valve body 5 before bending includes a substantially rectangular central portion 50 and a wheel plate portion 51 in contact with the left and right ends of the central portion 50. After punching a stainless steel plate, the central portion 50 is formed. It bends and bends both wheel plates 51 at right angles at the arrows in FIG. 3 (a) (see FIG. 3 (b)). Then, the holes 51a of both wheel plates 51 are connected to the rotating shaft 4. It is formed by fitting and fixing by welding. The central portion 50 has a rectangular hole 52 in the center, and the upper and lower portions of the hole 52 become a first valve portion 53 and a second valve portion 54.

Figure 4 shows a front view of plate 13.

Plate 13 has a circular base 13a and the inner end face of base 13a. It consists of an arc-shaped projection 13b, which is inserted into the right end opening 11a of the valve housing 11 of the housing 1 as described above, and closes that opening. . The stopper 13 b is disposed at the same position in the axial direction as the rotation stopping projection 45 of the ring 46, and as a result, the rotation angle range of the rotation stopping protrusion 45 and the rotation shaft 4 is limited to the stop. It is determined by the open angle of both ends of the wrapper 13b.

Figure 5 shows a schematic front view of the rotary solenoid 6.

By controlling the magnitude and direction of the current flowing through the coil 61, the amount of magnetic flux flowing through the magnetic circuit composed of the yoke 62 and the core 64 composed of a soft magnetic material, respectively, changes. As a result, the center position and the size of the magnetic pole facing the opening 62b of the base 62a of the yoke 62 change. As a result, these magnetic poles attract or repel the magnetic poles formed on the permanent magnet 63 fixed to the rotating shaft 4, and eventually control the magnitude and direction of the current flowing through the coil 61. Therefore, the permanent magnet 63 and the rotating shaft 4 rotate.

Figure 6 shows a developed view of the collar 2 before bending.

The collar 2 is made of a rectangular thin plate, and has a pair of curved sides 20 which are long sides and are curved sides, and a pair of non-curved sides 21 which are non-curved sides.

A notched linear groove 24 is formed at a predetermined distance inward from the four corners of the collar 2 in the direction of the non-curved side 21 and in the direction of extension of the curved side 20. Four elastic protrusions 25 protruding in the direction of the curved side 20 are formed at the corners. At the center in the direction of the non-curved side 21 1, in the direction of extension of the curved side 20, the outflow port 15 a, the concave part 26 with a depth of about 0.5 mm 26, the outflow port 14 a, A recess 27 having a depth of about 0.5 mm and an inflow port 23 are formed. The recesses 26 and 27 are provided for receiving foreign matter. The base of the elastic projection 25 (arrow portion in FIG. 6) is bent within a range in which the spherical bearing 3 can be press-fitted (see FIG. 7). The other part of the color 2 is cylindrically curved as shown in Fig. 7, and the two non-curved sides 2 1 A gap d is formed between them. The important point here is that the outflow port 14a is opened in the middle of each elastic projection 25 in the direction of the curved side 20.

In assembling, as described above, the collar 2, the ball bearing 3, the rotating shaft 4, the valve body 5, and the ring 46 are assembled in advance to form a subassembly. At this time, the elastic projections 25 of the collar 1 are elastically deformed to the outer peripheral side, and as a result, the elastic projections 25 strongly press the outer peripheral surface of the ball bearing 3, and the collar 2 and the ball bearing 3 are strong. To join. Also, even if a clearance occurs due to a difference in the coefficient of thermal expansion between the inner peripheral surface of the valve housing portion 11 and the outer peripheral surface of the collar 2, the elastic projections 25 remain Since the ball bearing 3 is urged in the direction of the outflow port 14a to return to the original position with respect to the portion near the non-curved side 21 of the collar 2, the outflow port 14a side The relative position between the inner peripheral surface of the valve section 11 and the outer peripheral surface of the valve element 5 does not change, and the clearance during this period is constant.

Therefore, the non-curved side of the color 2 is notwithstanding the addition of clarity due to the difference in thermal expansion coefficient between the valve housing 11 made of resin and the collar 2 made of stainless steel. 2 1 extends to the outer periphery to absorb the increase in clearance between the valve housing 11 and the color 2. Even if the non-curved side 21 of the force roller 2 expands, the arrangement of the elastic projections 25 causes the ball bearing 3 to move in the direction of the main outflow hole 14 having a larger sectional area than the sub outflow hole 15. Biasing, so that the increase in clearance between the valve element 5 and the outflow port 14a can always be reduced, and leakage when the valve is closed can be reduced. In this embodiment, the color 2 and the valve element 5 are made of the same stainless steel. However, for example, when the thermal expansion coefficients of the two are different, the inner peripheral surface of the color 12 is similar to the above. Clearance occurs between the valve body 5 and the outer peripheral surface of the valve body 5, but also in this case, leakage when the valve is closed is reduced due to the eccentricity of the rotating shaft 4 due to the bias of the elastic projections 25. can do. In addition, even when a clearance is originally generated between the inner peripheral surface of the color 2 and the outer peripheral surface of the valve element 5, the eccentricity of the rotating shaft 4 due to the biasing of the elastic projection 25 is also considered. As a result, leakage when the valve is closed can be reduced. For this reason, even if the above-mentioned clearance is formed slightly larger, the leakage can be kept within an allowable range.

Next, FIG. 8 shows a drive circuit 7 for driving a monolithic solenoid 6 and FIG. 8 shows an AC type, in which a P-channel MOS power transistor T1 and an N-channel MOS power transistor are used. The output terminal of the inverter II, which is formed by connecting the transistor T2 in series, the P-channel MOS power transistor T3 and the N-channel MOS power transistor T4. These are connected in series to the output terminal of I2 and the output terminal of I2, and are individually connected to both ends of the connector 61 of the resource solenoid 6. As is well known, when the input voltage VI of the inverter I1 is at a high level and the input voltage V2 of the inverter I2 is at a high level, the transistors T3 and A current flows through the transistor 61 through the transistor T2, and the input voltage V1 of the inverter I1 is at a low level and the input voltage V2 of the inverter I2 is at a high level. At this time, a reverse current flows through the transistor 61 through the transistor T1 and the transistor T4. In the normal flow control range (Q min to Q max), the current flowing to the coil 61 is controlled by the duty ratio control of the input voltage VI and the input voltage V 2 having the opposite phase, and as a result, The permanent magnet '63 rotates in response to the current flow.

More specifically, when the energizing current is 0, the N pole and the S pole of the permanent magnet 63 stand still in the state of FIG. 5, which is the angular position where the air gap is minimized. When the current is gradually increased in the direction of the coil 61, the N and S poles of the permanent magnet 63 are formed facing the opening 62b of the yoke 62. N and S poles are attracted and repelled, and are rotated clockwise from the air gap minimum angle position to the rotation angle position according to the current duty ratio. Rotate. If the energizing direction is reversed, the motor naturally rotates counterclockwise from the minimum air gap angle position to the rotation angle position corresponding to the duty ratio of the current according to the same principle.

Hereinafter, the features of the apparatus of this embodiment will be described with reference to FIGS. 9 to 11 showing a radial cross section of the valve housing 11 and FIG. 12 showing the relationship between the air flow rate and the duty ratio of the input voltage. The parts will be described. However, the sectional shape of the valve housing portion 11 of the housing 1 is schematically illustrated for simplicity. In addition, the valve body 5 is also schematically illustrated for simplicity without having to have the exact shape shown in FIG. 3 (b).

In FIG. 9, the input voltage VI of the drive circuit 7 is set to a high level at a duty ratio of 100% (duration ratio is set to 100%), and the input voltage V2 is set to a duty ratio of 0%. The high level is set at 0% (duty ratio is 0%). At this time, as described above, the protrusion 45 comes into contact with one end of the flange 45, and the valve element 5 is at the first final opening position. The first valve portion 53 of the valve element 5 has the main outlet hole 14 opened halfway, whereby the flow rate of the air flowing out of the main outlet hole 14 becomes the intermediate value Q1. On the other hand, the second valve portion 54 of the valve element 5 completely closes the sub-outlet 15, whereby the flow rate of the air flowing out from the sub-outlet 15 becomes the minimum value Q′min.

After that, the input voltage VI of the drive circuit 7 is gradually reduced from the on-duty ratio of 100% to 0%, and the input voltage V2 is kept at the duty ratio of 0%, that is, at the one-level level. The current flowing to the inverter I1 via the I2 coil 61 gradually decreases from the full load current to zero at last. As a result, the valve element 5 rotates counterclockwise in the figure, the first valve portion 53 gradually narrows the main outlet hole 14, and the amount of air flowing out of the main outlet hole 14 decreases, The value is Q min. Then, after the rear end face of the first valve portion 53 and the rear end A of the main outflow hole 14, the main outflow hole 14 starts to open again, and the air flow flowing out of the main outflow hole 14 is It increases to Q2. On the other hand, the second valve portion 54 starts to open the sub-outlet 15 and finally opens completely, The flow rate of the air flowing out of the outlet hole 15 gradually increases and reaches the maximum value Q'max.

FIG. 10 shows a state in which the on-duty ratios of the input voltages V I and V 2 of the drive circuit 7 are both 0% (one-level). That is, in this state, the current flowing through the coil 61 is zero. The valve element 5 is in the initial angular position (intermediate opening position), the air flow rate flowing out of the main outlet port 14 is Q 2, and the air flow rate flowing out of the sub outlet port 15 is Q′max. . After that, the on-duty ratio of the input voltage VI of the drive circuit 7 is kept at 0%, and the on-duty ratio of the input voltage V2 is increased from 0% to 100%. The current flowing to the inverter I2 via the input and output terminals 61 gradually increases from 0 and finally reaches the full load current. As a result, the valve element 5 rotates counterclockwise from the initial angular position (intermediate opening position) of the current 0 shown in FIG. 10, and the first valve portion 53 gradually opens the main outlet hole 14, The flow rate of air flowing out of the main outlet 14 increases and reaches the maximum value Q max. After that, the second valve section 54 starts to throttle the main outlet port 14, and when the on-duty ratio of the input voltage V 2 becomes 100%, the air flowing out of the main outlet port 14 becomes The flow rate becomes the intermediate value Q 3. On the other hand, the secondary outlet 15 remains open.

The protrusion 45 is designed to contact the end face of the stopper 13b at an on-duty ratio of about 90% in either direction of the current flow, and the angular position of the valve body 5 at this time. Are the final angular positions in the present invention.

Therefore, according to the device of the present embodiment, the air flow rate becomes the intermediate flow rate Q 2 when the power is cut off, and the air flow rate becomes the intermediate flow rate Q 1 or Q 3 when the power is turned on in either direction. In the end, even if an energization interruption fault or an uninterruptible failure occurs, the air flow rate does not reach the minimum value Q min or the maximum value Q max, and the engine is operated, for example, during running ( The output does not suddenly increase or decrease during the normal air flow.

In this example, two outflow holes, the main outflow hole 14 and the sub outflow hole 15 are used. However, a single outlet may be used. (Modification)

In the above-described embodiment, the cylindrical projection 2 5 is formed as a cylindrically curved collar 2. However, the elastic projection may urge the ball bearing 3 in the direction of the outflow hole. An elastic body may be interposed between the housing 1 and the inner peripheral surface. Further, the collar 2 can be formed in a completely cylindrical shape. Industrial applicability

As described above, the flow control rotary valve according to the present invention can be used as an intake air flow control valve for an internal combustion engine.

Claims

The scope of the claims

1. A rotatable support by a frame body having a valve chamber with an inflow hole and an outflow hole opened at the center of the inner peripheral surface in the bow direction, and a pair of bearings fitted to both ends of the inner peripheral surface. A flow control rotary valve comprising: a rotating shaft that is fixed to the rotating shaft; and a valve body that is housed in the valve chamber and that adjusts an opening degree of the hole by rotation.

By providing an urging means for urging the bearing on one side of the inner peripheral surface of the frame, a change in clearance between the valve element and the inner peripheral surface of the frame due to thermal expansion is provided. A flow control rotary valve characterized by reducing the number of rotations.

2. A plurality of the outflow holes are provided, and the urging means is provided on the inner peripheral surface side of the frame in which the outflow hole having the largest cross-sectional area is formed. 2. The flow control rotary valve according to claim 1, wherein the bearing is biased.

3. A resin housing having a valve chamber with an inflow hole and an outflow hole opened at the axially central portion of the inner peripheral surface, and the valve chamber having an opening at a position corresponding to the both holes to cover the valve chamber. A metal collar having a pair of bearings fitted at both ends while being in close contact with the inner peripheral surface of the housing; and a rotatably supported rotatably by the pair of bearings. A flow control rotary valve, comprising: a shaft; and a valve body fixed to the rotary shaft, housed in the valve chamber, and adjusting an opening degree of the hole by rotation.

By providing a biasing means for biasing the bearing on one side of the inner peripheral surface of the collar, a change in the clearance between the valve element and the inner peripheral surface of the collar due to thermal expansion is reduced. A flow control rotary valve characterized by a reduction.

4. The urging means is an elastic projection provided integrally with the color, which is located at a fitting portion of the pair of bearings and urges the pair of bearings. 3. The flow control rotary valve according to 3.

5. The collar has a cylindrical shape in which a pair of ends are opposed to each other with a gap therebetween, whereby the pair of ends are elastically deformed, and an inner peripheral surface of the housing is formed. The flow control rotary valve according to claim 4, wherein the rotary valve is in close contact with the flow control rotary valve.

6. In the flow control rotary valve that rotates the valve body by energizing the coil,

A resin housing having a valve chamber for accommodating the valve body and having an inflow hole and an outflow hole opened in a circumferential direction, and a coil chamber for accommodating the coil; and both housing holes And a pair of bearings provided at both ends, and a metallic material closely contacted with the inner peripheral surface of the housing so as to cover the valve chamber of the housing. Color and

A flow control rotary valve characterized by comprising:

7. The urging means is a projection provided on the collar and capable of being elastically deformed, and the projection urges the bearing toward the inner peripheral surface having the opening of the collar. The flow control rotary valve according to claim 6, wherein

8. The color has a cylindrical shape in which a pair of ends are opposed to each other with a gap therebetween, whereby the pair of ends is elastically deformed, and is closely contacted with an inner peripheral surface of the housing. 7. The flow control rotary valve according to claim 6, wherein