JP2015218763A - Flow regulating valve - Google Patents

Abstract

A flow rate control valve capable of ensuring good sealing performance of a seal member interposed between a communication port and a valve body. SOLUTION: First to third outlets communicating with the inside and outside of a housing 1, first to third openings communicating with the inside and outside of a valve body 3 rotatably accommodated on the inner peripheral side of the housing 1, In the flow control valve in which the seal member S1 that seals between the two is urged toward the valve body 3 by the spring SP, the housing SP is separated from the seating surface 33 of the spring SP on the end surface on the spring SP side of the seal member S1. 1 is provided with a pressure receiving surface 35 for receiving the pressure of the cooling water flowing in from the inside of 1 to urge the seal member S1 toward the valve body 3 side. [Selection] Figure 7

Description

  The present invention relates to a flow rate control valve used for controlling the flow rate of cooling water for automobiles, for example.

  For example, as a conventional flow control valve applied to the flow control of cooling water for automobiles, for example, the one described in Patent Document 1 below is known.

  That is, this flow control valve controls the amount of polymerization between the communication port that communicates the inside and outside of the housing and the valve hole that is formed through the peripheral wall of the substantially cylindrical valve body that is rotatably accommodated in the housing. By controlling the flow rate of the fluid, the gap between the communication port and the valve body is sealed between the communication port and the valve body when the valve is closed (when the communication port and the valve hole are not polymerized). A seal member is interposed.

  The seal member is slidably accommodated on the inner end side of the communication port, and is slidably contacted with the valve body by being urged to the valve body side by the urging member. In such a configuration, a known O-ring is fitted on the outer peripheral portion of the seal member, and the O-ring seals a minute gap formed between the outer peripheral surface of the seal member and the inner peripheral surface of the communication port. Thus, the leakage of fluid through the minute gap is suppressed.

Japanese Patent No. 3130785

  However, in the conventional flow control valve, since the O-ring is arranged in the minute gap, the hydraulic pressure of the fluid flowing into the minute gap causes the seal member to move to the outer end side, that is, the valve via the O-ring. As a result, the urging force of the seal member is reduced, and there is a possibility that sufficient sealing performance by the seal member cannot be secured.

  The present invention has been devised in view of such technical problems, and provides a flow control valve that can ensure good sealing performance of a seal member interposed between a communication port and a valve body. It is aimed.

  The present invention controls the inner circumferential side of the valve body by controlling the overlapping state of the communication port that communicates the inside and the outside of the housing and the valve hole that communicates the inside and the outside of the valve body rotatably accommodated in the housing. Is a flow control valve that controls the flow rate of fluid flowing out or inflowing through the valve hole and the communication port, and is slidably accommodated at the inner end side of the communication port, and the communication port and the valve body A first seal member that seals between the first seal member, a support member that is disposed opposite to the first seal member on an outer end side of the communication port, and serves to support the first seal member; the first seal member; A biasing member that is interposed between opposing portions of the support member and biases the first seal member toward the valve body, and a radial direction between the inner peripheral surface of the communication port and the outer peripheral surface of the first seal member The fluid introduction formed for the purpose of introducing the fluid from within the housing And a surface of the first seal member facing the support member separately from the seating surface of the biasing member, and the pressure of the fluid introduced from the fluid introduction portion acts to And a pressure receiving surface for urging the valve body side.

  According to the present invention, by causing the fluid in the housing introduced through the fluid introduction portion to act on the pressure receiving surface, in addition to the urging force of the urging member, the first seal member is also moved to the valve body side by the pressure of the fluid. Can be energized. Thereby, the favorable sealing performance by this 1st sealing member is securable.

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a system configuration diagram of an automotive cooling water circulation system showing a first embodiment of a flow control valve according to the present invention. It is a disassembled perspective view of the flow control valve concerning the present invention. It is a front view of the flow control valve shown in FIG. FIG. 4 is a sectional view taken along line AA in FIG. 3. FIG. 4 is a sectional view taken along line BB in FIG. 3. It is a longitudinal cross-sectional view of the fail safe apparatus shown in FIG. It is a principal part enlarged view of FIG. It is a perspective view showing the valve body simple substance shown in Drawing 2, and (a)-(c) is a figure showing the state seen from another viewpoint, respectively. It is a figure explaining the operating state of the flow control valve concerning the present invention, (a) is the state where only the 2nd outlet was connected, (b) is the state where all the outlets are out of communication, (c) Is a state in which only the first discharge port is in communication, (d) is a state in which the first and second discharge ports are in communication, and (e) is a development view of the valve body housing portion showing a state in which all the discharge ports are in communication. . The sealing structure of the conventional flow control valve is shown, (a) is a longitudinal sectional view showing the sealing structure, and (b) is an enlarged view of the main part of FIG. It is a principal figure which concerns on the 1st modification of 1st Embodiment of this invention. It is a principal figure which concerns on the 2nd modification of 1st Embodiment of this invention. It is a principal figure concerning 2nd Embodiment of this invention. It is a principal figure which concerns on the 1st modification of 2nd Embodiment of this invention.

  Embodiments of a flow control valve according to the present invention will be described below with reference to the drawings. In the following embodiments, the flow control valve according to the present invention will be described as an example in which the flow control valve according to the present invention is applied to a circulating system for automotive cooling water (hereinafter simply referred to as “cooling water”) similar to the conventional one.

[First Embodiment]
1 to 9 show a first embodiment of a flow control valve according to the present invention, and this flow control valve CV is disposed on the side of a cylinder head CH of an engine EG as shown in FIG. The cooling water pressurized by the WP and introduced from the cylinder head CH through the introduction path L0 to the heating heat exchanger HT, the oil cooler OC, and the radiator RD side through the first to third pipes L1 to L3, respectively. It distributes and controls each flow rate.

  That is, as shown in FIGS. 2 to 4, the flow rate control valve CV accommodates a deceleration mechanism having an elliptical cross section that extends in the width direction on one end side that is opposite to the cylinder head CH. A housing 1 in which a substantially cylindrical valve body housing portion 13 is connected to the inner surface of the speed reduction mechanism housing portion 14 in the form of being biased toward one end in the width direction of the speed reduction mechanism housing portion 14, and the valve body housing portion 13. The rotary shaft 2 is inserted between the speed reduction mechanism housing portion 14 and is rotatably supported by a bearing 6 provided between the portions 13 and 14, and one end portion of the rotary shaft 2. A substantially cylindrical valve body 3 which is rotatably mounted and fixed, and is rotatably accommodated in the valve body accommodating portion 13, and an output shaft 4b of the valve body accommodating portion 13 in parallel with the output shaft 4b. The reduction so as to face the inside of the other end in the width direction of the accommodating portion 14. An electric motor 4 that is attached and fixed to the inner side surface of the mechanism housing portion 14 and drives the valve body 3, and is interposed between the output shaft 4 b of the electric motor 4 and the rotary shaft 2, and the output shaft of the electric motor 4. The speed reducing mechanism 5 mainly reduces the rotational speed of 4b and transmits it to the rotating shaft 2.

  The housing 1 is cast from an aluminum alloy material, and mainly includes a first housing 11 that constitutes the valve body accommodating portion 13 and a second housing 12 that mainly constitutes the speed reduction mechanism accommodating portion 14. The two housings 11 and 12 are sandwiched and fixed by a plurality of U-shaped clips 7 fitted to the outer peripheral edge.

  The first housing 11 has an opening 10 formed at one end thereof, which is a main communication port that communicates with the cylinder head CH and introduces cooling water from the cylinder head CH. It is fixedly attached to the cylinder head CH via the first flange portion 11a provided. Further, the other end side of the first housing 11 is closed by an end wall 11b that separates the speed reduction mechanism accommodating portion 14, and via a second flange portion 11c configured integrally with the end wall 11b. It is joined to the second housing 12. In addition, a shaft insertion hole 11d for inserting and supporting the rotary shaft 2 is formed through the end wall 11b in the region on one end side in the width direction, and the inner end (output) of the electric motor 4 is formed in the region on the other end side. A motor insertion hole 11e into which the end portion on the shaft 4b side) is inserted and held is formed through.

  The said valve body accommodating part 13 is set to the predetermined internal diameter in the predetermined circumferential direction position in the outer peripheral part, as shown in FIGS. 1-5, and is connected with the said 1st-3rd piping L1-L3. The first to third discharge ports E1 to E3, which are a plurality of substantially cylindrical communication ports provided for the above, are formed to project in the radial direction. That is, the first outlet E1 having a medium diameter that communicates with the heating heat exchanger HT and the second outlet E2 having a small diameter that communicates with the oil cooler OC extend along the axial direction of the valve body housing portion 13. The first outlet E1 is biased toward the end wall 11b, and the second outlet E2 is offset toward the inlet 10 side. On the other hand, the large-diameter third discharge port E3 communicating with the radiator RD is a circumferential position different from the first and second discharge ports E1 and E2, and the first and second discharge ports in the axial direction. It is provided so as to be polymerized with the outlets E1 and E2.

  The first to third discharge ports E1 to E3 are provided with large-diameter first to third adapter holding portions E1a to E3a at the outer peripheral end portions so as to have a stepped diameter increase. The substantially cylindrical first to third adapters A1 to A3 used for connection with the pipes L1 to L3 are inserted into the inner peripheral surfaces of the holding parts E1a to E3a from the outer ends of the discharge ports E1 to E3. (Press fit) It is fixed. And at the edge part of the inner peripheral side of each said discharge port E1-E3, each discharge port E1-E3 and the outer peripheral surface of the valve body 3, ie, each said adapter A1-A3 and the valve body 3 (after-mentioned 1st-1st). Sealing means SX for sealing the space between the third axial regions X1 to X3) is provided.

  In addition, since all the configurations of the sealing means SX in the first to third discharge ports E1 to E3 are common, the third discharge port E3 will be described below based on FIGS. 6 and 7 for convenience of explanation. Details of the configuration will be described by exemplifying only the sealing means SX.

  The sealing means SX is slidable in a manner to face the third adapter A3 in a third seal accommodating portion E3b provided in a step-reduced diameter at the inner peripheral end of the third discharge port E3. A substantially cylindrical seal member S1 (corresponding to the first seal member of the present invention) that seals between the third adapter A3 and the valve body 3, and the seal member S1 and the third adapter A3. And a spring SP that is an urging member interposed between the two, and by urging the seal member S1 toward the valve body 3 by the spring SP, the sealing performance between the three and S1 is improved. Improvements are being made.

  As described above, the seal member S1 has a substantially cylindrical shape, and an inner peripheral portion thereof is configured as a flow path constituting portion 31 that provides cooling water flow. A substantially tapered valve body sliding contact portion 32 that is in sliding contact with a third axial direction region X3 described later is provided. On the other hand, on the other end side of the seal member S1, a flat seating surface 33 used for seating on one end side of the spring SP is formed on the outer peripheral side, while a well-known O-ring S2 is formed on the inner peripheral side. A step-shaped concave portion 34 for accommodating (corresponding to the second seal member according to the present invention) is formed, and the O-ring S2 is always pressed against the end surface of the step-shaped concave portion 34 facing the third adapter A3. Thus, a pressure receiving surface 35 is formed through the O-ring S2 for use in receiving a cooling water pressure, which will be described later.

  Here, the sum of the radial width C1 of the pressure receiving surface 35 and the radial width C0 of the seating surface 33 is larger than the radial width C2 of the distal end side working surface 37 on which the water pressure acts on the distal end side of the seal member S1. Are set to be relatively large. Here, the said front end side action surface 37 means the surface which faced the valve body accommodating part 13 comprised in the radial direction outer side from the contact point P of the sealing member S1 with respect to the valve body 3 (refer FIG. 7).

  Further, the outer diameter of the seal member S1 is set to be slightly smaller than the inner diameter of the third discharge port E3, and there is a predetermined minute gap between the inner peripheral surface of the third discharge port E3. A fluid introduction part 36 is provided that serves to introduce cooling water in the housing 1 (valve element accommodation part 13). Thereby, the cooling water that has acted on the sliding contact portion of the sealing member S1 with the valve body 3 (third axial direction region X3 described later) introduces the fluid from the sliding contact portion along the outer peripheral surface of the sealing member S1. It can flow into the portion 36.

  The third adapter A3 is provided so as to face the outside of the third discharge port E3, and has a pipe connection part 41 for connection to the third pipe L3, and a step expanding to the base end side of the pipe connection part 41. A press-fit portion 42 that is formed in a diameter and is press-fitted and fixed to the adapter holding portion E3b. The portion 43 and the support portion 43 are provided so as to overlap with the step-shaped recess 34 of the seal member S1 by extending in a step-reduced shape, and hold the O-ring S2 together with the step-shaped recess 34 And a seal holding portion 44 to be configured.

  On the outer peripheral surface of the press-fit portion 42, a liquid-tight seal is provided between the outer peripheral surface of the press-fit portion 42 and the adapter holding portion E3b at an axial position near the spring SP (a seating surface 46 described later). A seal holding portion 45 that accommodates and holds the well-known O-ring S3 (corresponding to a third seal member according to the present invention) is cut out along the circumferential direction. That is, the O-ring S3 accommodated in the seal holding part 45 is pressed against the adapter holding part E3b so that the outflow of cooling water introduced from the fluid introduction part 36 described later is blocked. It has become.

  Between the press-fit portion 42 and the support portion 43, a flat seating surface 46 is formed to be used for seating on the other end side of the spring SP so as to face the seating surface 33 of the seal member S1, Between the facing surface of the seating surface 46 and the seating surface 33 of the seal member S1, a spring housing space 47 that constitutes a housing space for the spring SP that faces the flow path component 31 is formed. Further, the support portion 43 is set to have an outer diameter slightly smaller than the inner diameter of the spring SP, and is configured to be received in the stepped recess 34. Accordingly, when the third adapter member A3 is attached (inserted), the O-ring S2 can be pushed in by the support portion 43, and the O-ring S2 is inserted into the step-shaped recess 34. After the attachment, the spring SP can be appropriately held by supporting the inner peripheral portion of the spring SP even when a cooling water pressure described later acts.

  The seal holding portion 44 is offset from the inner peripheral surface (flow path constituting portion 31) of the seal member S1 on the inner peripheral side, and the spring accommodating space is provided between the seal holding portion 44 and the stepped recess 34 of the seal member S1. The seal accommodating space 48 that constitutes the accommodating space of the O-ring S2 facing the 47 is formed. That is, cooling water flows into the seal housing space 48 from the valve body housing portion 13 through a series of flow paths 50 including the seal housing space 48, the spring housing space 47, and the fluid introducing portion 36. Thus, the inflowing cooling water is blocked by the O-ring S2 accommodated and held in the seal accommodating space 48.

  Further, the side of the first discharge port E3 in the first housing 11 can communicate with the valve body accommodating portion 13 and the third discharge port E3 in the event of an emergency in which the valve body 3 cannot be driven, such as when the electrical system fails. Even if the fail-safe device 20 is provided and the valve body 3 is stationary, it is possible to prevent overheating of the engine EG by ensuring the supply of cooling water to the radiator RD. Yes. As shown in FIGS. 1 and 6, the fail-safe device 20 mainly includes a thermo element 21, a valve plate member 22, a coil spring 23 and a plug 24, and is a known thermostat such as a wax pellet type. It operates on the same principle.

  Specifically, one end side that is the outer end side opens to the outside at the side portion of the third discharge port E3 in the first housing 11, and an inflow hole 15a that communicates with the valve body housing portion 13 is formed through the other end side. The cylindrical valve accommodating portion 15 is adjacently provided, and an outflow hole 15b communicating with the third discharge port E3 is formed in the side portion of the valve accommodating portion 15 so as to penetrate therethrough. One end side opening of the valve accommodating portion 15 is closed by the plug 24, and the other end side of the valve accommodating portion 15 is reduced in diameter in a step shape at an axial position on the inner end side than the outflow hole 15b. The formed thermo accommodating portion 15c is provided, and the thermo element 21 is accommodated and disposed in the thermo accommodating portion 15c. The valve plate member 22 is disposed so as to close the opening on the outflow hole 15b side of the thermo accommodating portion 15c, and a coil spring 23 is mounted between the valve plate member 22 and the plug 24, When the temperature exceeds a predetermined temperature, the wax filled in the thermo element 21 expands to cause the rod 21a to project, whereby the valve plate member 22 is pushed away against the biasing force of the coil spring 23. The inflow hole 15a and the outflow hole 15b communicate with each other. In addition to the temperature rise, when the pressure of the cooling water exceeds a predetermined pressure, the valve plate member 22 is pushed away against the urging force of the coil spring 23, whereby the inflow hole 15a and the outflow hole 15b. And communicate with each other.

  As shown in FIGS. 2 to 4, the second housing 12 is formed in a U-shaped cross section in which one end side facing the first housing 11 is open, and this opening is the second flange. The speed reduction mechanism accommodating portion 14 is configured to be connected to the first housing 11 by fitting with a convex portion erected on the outer peripheral edge of the portion 11c. When the housings 11 and 12 are joined together, an annular seal member SL is interposed between the convex portion of the first housing 11 and the opening of the second housing 12 to accommodate the speed reduction mechanism. The inside of the part 14 is configured to be liquid-tight.

  The rotary shaft 2 is rotatably supported by the bearing 6 accommodated in the shaft insertion hole 11d via a bearing portion 2a provided at an intermediate portion in the axial direction. One end portion of the rotary shaft 2 is configured as a valve body mounting portion 2b that is set to have substantially the same diameter as the bearing portion 2a and serves for mounting and fixing the valve body 3, and the other end portion is configured to be the bearing. The gear mounting portion 2c is formed as a relatively small diameter with respect to the portion 2a and serves to mount and fix a third gear G3 described later in the speed reduction mechanism 5. Further, a space between the bearing portion 2a and the valve body mounting portion 2b is configured as a large-diameter seal portion 2d having a stepped diameter, and a pair of first and second portions are provided on the outer periphery of the seal portion 2d. Seal rings R1 and R2 are arranged in series, and the flow of the cooling water in the valve body housing portion 13 into the speed reduction mechanism housing portion 14 is suppressed by the seal rings R1 and R2.

  Here, each of the seal rings R1 and R2 is preferably subjected to low friction treatment for reducing frictional resistance (sliding resistance) such as so-called fluororesin processing on each outer peripheral surface. Thereby, the sliding resistance of the rotating shaft 2 can be reduced, and the power consumption of the electric motor 4 can be reduced.

  In addition, the space between the seal rings R1 and R2 in the seal portion 2d is configured to face a drain hole 11f formed in a radial direction with respect to the shaft insertion hole 11d of the first housing 11, and the drain hole 11f. Thus, the cooling water leaked between the seal rings R1 and R2 beyond the seal portion by the first seal ring R1 from the valve body accommodating portion 13 side can be discharged to the outside.

  As shown in FIGS. 2, 4 and 8, the valve body 3 has an axial inlet 3 a at which one end in the axial direction takes in cooling water from the inlet 10 of the first housing 11 into the inner circumferential space. The other end is closed by the end wall 3b. A cylindrical shaft fixing portion 3c used for attachment to the rotary shaft 2 is formed through the central portion of the end wall 3b corresponding to the shaft center of the valve body 3 along the axial direction. It is press-fitted and fixed to the outer periphery of the valve body mounting portion 2b of the rotating shaft 2 through a metal insert member 3d provided integrally with the portion 3b.

  Further, the valve body 3 functions by rotating within an angular range of about 180 °, and is formed in a different shape according to the axial and circumferential regions thereof. That is, in the first half-circumferential region D1 facing the first and second discharge ports E1 and E2 of the valve body 3, the first axial region X1 in the first axial region X1 on the other axial end side (the end wall 3b side). A first opening in the shape of an elongated hole set to an axial width that overlaps with the first discharge port E1 in the axial direction at a first axial position P1 that is the same axial center as the first discharge port E1. A portion M1 is provided along the circumferential direction, and the second axial direction is the same axial center as the second discharge port E2 in the second axial region X2 on the other axial end side (the inlet 10 side). At the position P2, the circular second perfect circular opening M2a and the long hole-shaped second elliptical opening M2b set to the axial width that overlaps with the second discharge port E2 in the axial direction without excess or deficiency. A configured second opening M1 is provided. On the other hand, in the second semicircular region D2 facing the third discharge port E3 of the valve body 3, it becomes the same axial center as the third discharge port E3 in the third axial region X3 existing in the intermediate portion in the axial direction. A circular third opening M3 that overlaps with the third discharge port without excess or deficiency is provided at the third axial position P3. Each of the first to third axial regions X1 to X3 has a spherical cross section, that is, a curved surface having the same curvature C, and the curvature C is equal to the rotation radius of the valve body 3. It is comprised so that it may become the same.

  Here, in this embodiment, the valve hole which concerns on this invention is comprised by the said 1st-3rd opening part M1-M3, and each shape and circumferential direction position of these opening part M1-M3 are the rotation of the valve body 3. FIG. With the movement, it is set so that the communication state with the first to third discharge ports E1 to E3 is switched in the order of first to fifth states to be described later shown in FIG. 3, that is, the outer diameter of the valve body 3 is minimized.

  Further, the valve body 3 is configured such that the first to third axial regions X1 to X3 each have a spherical shape, so that there is a step at each boundary between the half-circumferential regions D1 and D2. Portions 3e and 3e are formed. Thereby, when rotating the said valve body 3, it becomes possible to regulate rotation by making each said level | step-difference part 3e and 3e into what is called a stopper. Each of these step portions 3e, 3e is inevitably provided for the configuration of the valve body 3, and by using this, there is no need to separately provide the stopper, and the cost is reduced.

  As shown in FIGS. 2 and 4, the electric motor 4 has an inner end portion (end portion on the output shaft 4 b side) of a motor housing 4 a that is an exterior thereof fitted into the motor insertion hole 11 e. It is fixedly attached to the first housing 11. The electric motor 4 is driven and controlled by a vehicle-mounted electronic controller (not shown), and the valve body 3 is controlled to rotate according to the vehicle operating state, thereby cooling water to the radiator RD and the like. Achieve proper distribution.

  The speed reduction mechanism 5 is fixed to the outer periphery of the output shaft 4b of the electric motor 4 so as to be integrally rotatable, and a first gear G1 which is a circular drive gear having a predetermined first tooth portion G1a formed on the outer periphery thereof; A predetermined second tooth portion G2a that is fixed to the outer periphery of a support shaft 9 that is rotatably supported at an intermediate position in the width direction of the first housing 11 so as to be integrally rotatable, and that can mesh with the first tooth portion G1a. A second gear G2, which is a formed circular intermediate gear, is fixed to the outer periphery of the gear mounting portion 2c of the rotary shaft 2 so as to be integrally rotatable, and the outer periphery of the second gear G2 can be meshed with the second tooth portion G2a. And a third gear G3 that is a substantially semi-circular driven gear in which the third tooth portion G3a is formed. With this configuration, the second gear G2 is rotationally driven based on the driving force of the electric motor 4 transmitted by the first gear G1, and the third gear G3 is predetermined by the driving force transmitted by the second gear G2. It will rotate in the angular range. At this time, each end of the third gear G3 in the circumferential direction abuts on an arcuate stopper portion 11g formed on the end wall 11b so as to protrude from the surface facing the second housing 12, thereby further increasing the third gear G3. The rotation is restricted.

  Hereinafter, a specific operation state of the flow control valve CV will be described with reference to FIG. In the description, in FIG. 9, the first to third openings M1 to M3 of the valve body 3 are indicated by broken lines, while the first to third discharge ports E1 to E3 of the first housing 11 are hatched. For example, the discharge ports E1 to E3 and the openings M1 to M3 are relatively identified for the sake of convenience by painting and displaying the state in which the two E1 to E3 and M1 to M3 communicate with each other.

  That is, the flow control valve CV is calculated based on the vehicle operating state, and the electric motor 4 is driven and controlled by the control current from the electronic controller (not shown) that is output, so that the flow control valve CV corresponds to the vehicle operating state. The rotational position (phase) of the valve body 3 is controlled so that the relative relationship between the discharge ports E1 to E3 and the openings M1 to M3 is as follows.

  In the first state shown in FIG. 9A, only the second opening M2 (M2a) is in a communication state, and the first and third openings M1 and M3 are in a non-communication state. Therefore, in the said 1st state, based on this communication state, cooling water is supplied only from the 2nd discharge port E2 to the oil cooler OC through the 2nd piping L2, and both said E2 and M2 are shifted and each superposition | polymerization is carried out. By changing the amount, the supply amount can be changed.

  After the first state, in the second state shown in FIG. 9B, all of the first to third openings M1 to M3 are not in communication with the discharge ports E1 to E3. Thus, in the second state, the cooling water is not supplied to any of the heating heat exchanger HT, the oil cooler OC, and the radiator RD.

  After the second state, in the third state shown in FIG. 9C, only the first opening M1 is in the communication state, and the second and third openings M2 and M3 are in the non-communication state. Therefore, in the said 3rd state, based on this communication state, cooling water is supplied only to the heating heat exchanger HT from the 1st discharge port E1 through the 1st piping L1, and both the said E1, M1 are shifted and each is shifted. The supply amount can be changed by changing the polymerization amount.

  After the third state, in the fourth state shown in FIG. 9D, only the third opening M3 is in a non-communication state, and the first and second openings M1 and M2 (M2b) are in a communication state. It becomes. Therefore, in the said 4th state, based on this communication state, it cools with respect to the heating heat exchanger HT and the oil cooler OC through the 1st, 2nd piping L1, L2 from the 1st, 2nd discharge port E1, E2, respectively. By supplying water and shifting both of these E1 to E2 and M1 to M2 to change the respective polymerization amounts, the supply amounts can be changed.

  After the fourth state, in the fifth state shown in FIG. 9E, all of the first to third openings M1 to M3 are in communication with the discharge ports E1 to E3. Therefore, in the said 5th state, cooling water is supplied with respect to all of the heating heat exchanger HT, the oil cooler OC, and the radiator RD, and these both E1-E3, M1-M3 are shifted and each polymerization amount is changed. As a result, the supply amount can be changed.

  Hereinafter, characteristic operation and effects of the flow control valve CV according to the present embodiment will be described based on FIGS. 6 and 7 in comparison with the configuration of the conventional flow control valve shown in FIG. 10 as a comparative example. . In FIG. 10 showing the conventional structure, the same components as those of the flow control valve CV will be described with the same reference numerals for the convenience of comparison. In the following, the sealing means SX related to the third discharge port E3 will be described as an example, but the same can be said for the other discharge ports E1 and E2, and therefore the third discharge port E3 and the third adapter A3. Etc. will be described simply as “discharge port E3”, “adapter A3”, and the like.

  First, in the seal structure in the conventional flow control valve shown in FIG. 10, as described above, the annular seal S4 is interposed between the seal member S1 urged toward the valve body 3 by the spring SP and the discharge port E3. Thus, the annular seal S4 suppresses the intrusion of the cooling water from the inside of the housing 1, and prevents the leakage of the cooling water through the radial gap CX between the sealing member S1 and the discharge port E3.

  For this reason, the cooling water flowing in through the radial gap CX (see the thick arrow in the figure) is blocked by the annular seal S4, so that the annular seal member S4 is surrounded by the cooling water pressure (on the adapter A3 side). As a result, the entire seal member S1 is pressed toward the adapter A3 side, that is, the side away from the valve body 3 via the annular seal member S4, resulting in deterioration of the sealing performance of the seal member S1. I was sorry.

  On the other hand, in the flow rate control valve CV according to the present embodiment, as shown in FIGS. 6 and 7, the sealing member S1 and the discharge port E3 are arranged without any sealing means between the radial directions, as described above. Since it is configured as the fluid introduction part 36 that constitutes the series of flow paths together with the spring accommodation space 47 and the seal accommodation space 48, it flows into the fluid introduction part 36 from the inside of the housing 1 (valve element accommodation part 13). The cooling water reaches the spring accommodating space 47 and the seal accommodating space 48 and is blocked by the O-rings S2 and S3 as indicated by thick arrows in FIG.

  Then, the pressure of the cooling water based on the weir acts on the O-ring S2, and the O-ring S2 presses the pressure receiving surface 35. In addition to the urging force of the spring SP, the cooling water It is possible to press the seal member S1 toward the valve body 3 also by water pressure. As a result, the adhesion between the seal member S1 and the valve body 3 (axial region X3) is improved, and it is possible to ensure the desired sealing performance without deteriorating the sealing performance as in the conventional structure. It becomes.

  In this seal structure, as described above, at least the total of the radial width C1 of the pressure receiving surface 35 and the radial width C0 of the seating surface 33 is larger than the radial width C2 of the distal end working surface 37. Therefore, the seal member S1 can be urged toward the valve body 3 against the water pressure acting on the distal end side acting surface 37, and the water pressure applied to the seal member S1. The effectiveness of the force is ensured.

  Thus, according to the flow rate control valve CV, no sealing means is provided between the sealing member S1 and the discharge port E3, and the cooling water is circulated to the proximal end side (the opposite side of the valve body 3) of the sealing member S1. Thus, the water pressure is applied to the pressure receiving surface 35 provided separately from the seating surface 33 on the base end side, so that in addition to the biasing force of the spring SP, the seal member S1 is also moved by the water pressure. As a result, it is possible to ensure good sealing performance of the seal member S1.

  Further, with such a configuration, the water pressure acts on not only the pressure receiving surface 35 but also the seating surface 33 on which the spring SP is seated in the water pressure action on the O-ring S2 (pressure receiving surface 35). Therefore, the water pressure can be substantially received by both the seating surface 33 and the pressure receiving surface 35, and the sealing performance can be further improved.

  Further, in the case of the flow rate control valve CV, the O-ring S3 is disposed in the axial position near the seating surface 46, so that the water pressure in the spring accommodating space 47 (series of flow paths 50) is reduced. As a result of being minimized and being able to apply a larger (maximum) urging force to the seal member S1, it is possible to ensure better sealing performance of the seal member S1.

  Moreover, there is also an advantage that the flow control valve CV can be configured at a lower cost by using general-purpose products such as the O-rings S2 and S3 as the second and third seal members, respectively.

  In the present embodiment, the O-rings S2 and S3 are used as examples. However, as the second and third seal members, any other annular seal member such as an X-ring can be applied. It is.

(First modification)
FIG. 11 shows a first modification of the first embodiment, in which the spring accommodating space 47 is enlarged by removing the support portion 43 for each adapter member A3. It is.

  Thus, by deleting the support part 43, there is a merit that the adapter member A3 can be easily formed (processed) because one step part constituting the support part 43 can be deleted.

(Second modification)
FIG. 12 shows a second modification of the first embodiment, wherein the stepped recess 34 is formed in a two-step configuration with respect to the seal member S1, so that the second step is the adapter. This is configured as an adapter accommodating portion 38 for accommodating the member A3.

  As shown in the figure, also in this structure, as in the first embodiment, at least the total of the radial width C1 of the pressure receiving surface 35 and the radial width C0 of the seating surface 33 is the tip side working surface. 37 is configured to be larger than the radial width C2.

  That is, in the present embodiment, the adapter holder A3 is accommodated in the adapter holder 38 provided in the seal member S1, so that the inner diameter of the seal holder 44, that is, the adapter member A3 of the adapter member A3 is accommodated. The inner diameter R2 is configured to be equal to or larger than the inner diameter R1 (substantially the same diameter in the present embodiment) of the flow path component 31 of the seal member S1.

  Thus, the inner diameter R2 of the adapter member A3 is set to be equal to or larger than the inner diameter R1 of the flow path component 31 of the seal member S1, so that the required inner diameter (flow path cross-sectional area) of the adapter member A3 is set. There is an advantage that it can be ensured and the generation of flow resistance based on the formation of the restriction by the adapter member A3 can be suppressed.

[Second Embodiment]
FIG. 13 shows a second embodiment of the flow rate control valve according to the present invention, in which the O-ring S2 in the first embodiment is abolished and cooled instead by a sealing means based on a so-called labyrinth structure. It is configured to suppress water leakage. The configuration other than the sealing means is the same as in the first embodiment.

  That is, in the present embodiment, seal constituent portions 39 and 49 that are superposed in multiple stages in the radial direction are provided on the base end sides of the seal member S1 and the adapter member A3, respectively. By adjusting a plurality of radial gaps C3 formed between 49, the cooling water flowing in from the fluid introduction part 36 is blocked.

  In this way, by adopting a configuration in which the sealing function is exhibited by the large number of radial gaps C3 that are polymerized in the radial direction, the amount of polymerization in the axial direction of the overlapping portion (both seal constituent portions 39 and 49) is relatively shortened. It becomes possible. As a result, the increase in the axial direction of the overlapping portion is suppressed, which can contribute to the downsizing of the flow control valve CV.

  In addition, the adapter member A3 has an inner diameter that is set to be equal to or larger than the inner diameter of the flow path component 31 of the seal member S1, thereby ensuring a necessary inner diameter (flow path cross-sectional area) of the adapter member A3. There is an advantage that the generation of flow resistance based on the formation of the restriction by the adapter member A3 can be suppressed.

(Modification)
FIG. 14 shows a modified example of the second embodiment, in which the respective seal constituent portions 39, 49 are configured to be superposed in a stepped manner in the axial direction. 49, the cooling water flowing in from the fluid introduction part 36 is blocked by adjusting a plurality of radial gaps C4 formed between the two.

  Thus, the radial width of the overlapping portion (both seal constituent portions 39, 49) is relatively shortened by adopting a configuration in which a sealing function is exhibited by a large number of radial gaps C4 formed in the axial direction. Is possible. As a result, the enlargement of the overlapping portion in the radial direction is suppressed, which can contribute to the downsizing of the flow control valve CV.

  In addition, the adapter member A3 has an inner diameter that is set to be equal to or larger than the inner diameter of the flow path component 31 of the seal member S1, thereby ensuring a necessary inner diameter (flow path cross-sectional area) of the adapter member A3. There is an advantage that the generation of flow resistance based on the formation of the restriction by the adapter member A3 can be suppressed.

  The present invention is not limited to the configuration of each of the above-described embodiments. For example, the size of the first to third discharge ports E1 to E3 and the shape, quantity, and arrangement of the first to third openings M1 to M3 ( (Circumferential position) and the like, as well as the specific configuration of the series of flow paths 50 and the arrangement of the O-rings S2 and S3, as long as the above-described effects can be achieved. It can be changed freely according to the specifications.

  Furthermore, in each of the above-described embodiments and the like, an example of application to the circulation system of cooling water has been described as an example of application of the flow control valve CV. However, the flow control valve CV is not limited to the cooling water, for example, lubrication Needless to say, the present invention is applicable to various fluids such as oil.

  Hereinafter, technical ideas other than those described in the scope of claims ascertained from the respective embodiments and the like will be described.

(A) In the flow control valve according to claim 5,
Both the second seal member and the third seal member are constituted by O-rings.

  In this way, by using a general-purpose product, it can be configured at a lower cost.

(B) In the flow control valve according to claim 5,
A flow rate control valve characterized in that a step portion configured to be able to support the inner peripheral portion of the biasing member is provided on the front end side of the support member so as to face the second seal member. .

  By setting it as this structure, an urging | biasing member can be stably hold | maintained by a step part, and it will also be used for insertion of a 2nd seal member by this step part.

(C) In the flow control valve according to claim 5,
The flow rate control valve according to claim 1, wherein the support member is formed in a straight shape on a tip side with respect to a seating surface of the biasing member.

  With this configuration, the shape of the support member can be simplified, and the manufacturing cost can be reduced.

(D) In the flow control valve according to claim 6,
The flow control valve according to claim 1, wherein an inner diameter of the support member is set to be equal to or larger than an inner diameter of the first seal member.

  By adopting such a configuration, there is an advantage that the flow resistance necessary for the fluid flowing through the inner peripheral side can be ensured and the flow resistance based on the formation of the restriction can be suppressed.

(E) In the flow control valve according to claim 7,
Each of the radial gaps between the overlapping portions is configured in a multi-stage overlapping manner in the radial direction.

  By setting it as this structure, the enlargement of the superposition | polymerization part of the axial direction is suppressed, and it can contribute to size reduction of a flow control valve.

(F) The flow control valve according to claim 7,
Each radial gap between the overlapping portions is configured in such a manner as to undergo multistage polymerization in the axial direction.

  By setting it as this structure, the enlargement of the superposition | polymerization part in the radial direction is suppressed, and it can contribute to size reduction of a flow control valve.

DESCRIPTION OF SYMBOLS 1 ... Housing 3 ... Valve body 33 ... Seating surface 35 ... Pressure receiving surface 36 ... Fluid introduction part A1-A3 ... 1st-3rd adapter member (support member)
E1 to E3 ... 1st to 3rd discharge port (communication port)
M1 to M3 ... 1st to 3rd openings (valve holes)
S1: Seal member (first seal member)
SP ... Spring (biasing member)

Claims (8)

By controlling the polymerization state of the communication port that communicates the inside and the outside of the housing and the valve hole that communicates the inside and the outside of the valve body that is rotatably accommodated in the housing, A flow rate control valve for controlling a flow rate of fluid flowing out or inflowing through a valve hole and a communication port,
A first seal member that is slidably housed on the inner end side of the communication port and seals between the communication port and the valve body;
A support member that is disposed opposite to the first seal member on the outer end side of the communication port, and serves to support the first seal member;
A biasing member interposed between opposing portions of the first seal member and the support member, and biasing the first seal member toward the valve body;
A fluid introduction part that is formed between the inner circumferential surface of the communication port and the outer circumferential surface of the first seal member and serves to introduce fluid from the housing;
The valve of the first seal member is provided on the surface of the first seal member facing the support member separately from the seating surface of the biasing member, and the pressure of the fluid introduced from the fluid introduction portion acts on the valve. A pressure receiving surface for biasing to the body side;
A flow control valve characterized by comprising: The front end side of the support member is configured to overlap with the inner peripheral side of the first seal member,
The flow rate control valve according to claim 1, wherein a second seal member for blocking a fluid introduced from the fluid introducing portion is interposed between the overlapping portions.   The surface of the first seal member facing the support member is formed by both the seating surface and the pressure receiving surface on which the pressure of the fluid introduced from the fluid introduction portion acts. The flow control valve described. Between the inner peripheral surface of the communication port and the outer peripheral surface of the support member is interposed a third seal member for blocking the fluid introduced from the fluid introduction portion,
The flow control valve according to claim 3, wherein the third seal member is disposed at an axial position in the vicinity of the biasing member.   The flow rate control valve according to claim 4, wherein the front end side of the support member is offset on the inner peripheral side so that a predetermined gap is formed between the overlapping portions.   The sum of the radial widths of the pressure receiving surface and the seating surface is set to be relatively larger than the radial width of the radially outer portion than the contact point of the first seal member with the valve body. The flow control valve according to claim 2, wherein the flow control valve is provided.   The front end side of the support member is configured to overlap with the inner peripheral side of the first seal member, and is configured to control the amount of leakage of the fluid introduced from the fluid introducing portion by a gap between the overlapping portions. The flow control valve according to claim 1, wherein: A main communication port provided in a valve body housing portion having a substantially circular cross section, which is used for introduction or discharge of cooling water, and the introduction or discharge of cooling water in the valve body housing portion communicating with the valve body housing portion from the radial direction. A housing having a plurality of communication ports to be provided for,
A substantially cylindrical valve body that is rotatably supported in the housing and has a plurality of openings in which a polymerization state with each communication port changes according to the rotation position;
An actuator for controlling the rotational position of the valve body;
A first seal member that is slidably housed and disposed on the inner end side of each communication port, and seals between each communication port and the valve body;
A support member that is disposed opposite to the first seal member on the outer end side of each communication port, and serves to support the first seal member;
A biasing member interposed between opposing portions of the first seal member and the support member, and biasing the first seal member toward the valve body;
A fluid introduction part that is formed between the inner circumferential surface of each communication port and the outer circumferential surface of the first seal member and serves to introduce fluid from within the housing;
The valve of the first seal member is provided on the surface of the first seal member facing the support member separately from the seating surface of the biasing member, and the pressure of the fluid introduced from the fluid introduction portion acts on the valve. A pressure receiving surface for biasing to the body side;
A flow control valve characterized by comprising:

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