JP7064825B2 - Flow control valve - Google Patents

Description

The present invention relates to a flow control valve.

As a conventional flow rate control valve, for example, the one described in the following Patent Document 1 is known.

This flow control valve has a main communication port formed through an opening in the peripheral wall of the cylindrical housing, a communication port for communicating with a radiator, a bypass and a heater, and a peripheral wall of a cylindrical valve body rotatably housed in the housing. It has an opening corresponding to each communication port formed in the opening. That is, this flow rate control valve controls the distribution and flow rate of the cooling water according to the polymerization state of each communication port and each opening.

Further, in this flow control valve, when changing the combination of each communication port and each opening, a mode in which the communication state of other communication ports is changed while the communication with the heater is always cut off such as on a warm day. It is designed to switch between a mode in which the communication state of other communication ports is changed while the communication is always in communication with the heater, such as on a cold day.

Japanese Patent No. 4741794

However, the conventional flow rate control valve has a configuration in which the openings are arranged in series in the rotation axis direction of the valve body. Therefore, there is a problem that the valve body becomes large in the direction of the rotation axis.

The present invention has been devised in view of such technical problems, and an object of the present invention is to provide a flow rate control valve capable of suppressing an increase in size of a valve body in the rotation axis direction.

One aspect of the present invention is the first state in which the third communication port of the housing and the third opening of the valve body are constantly communicated with each other, and the communication state of the first opening and the second opening of the valve body changes. A flow rate control having a second state in which the third communication port of the housing and the third opening of the valve body are always non-communication and the communication state of the first opening and the second opening of the valve body changes. In the valve, the first opening and the second opening are formed so as to overlap at least a part in the rotation axis direction of the valve body at different circumferential positions on the outer peripheral surface of the valve body, and the third opening. The opening is formed in parallel with the first opening in the rotation axis direction of the valve body.

According to the present invention, it is possible to suppress an increase in the size of the valve body in the rotation axis direction.

It is a block diagram which showed the structure of the circulation circuit of the cooling water for automobiles to which the flow rate control valve which concerns on this invention is applied. It is a modification of the cooling water circulation circuit shown in FIG. It is a block diagram which showed the other structure of the circulation circuit of the cooling water for automobiles to which the flow rate control valve which concerns on this invention is applied. It is an exploded perspective view of the flow rate control valve which concerns on this invention. It is a perspective view of the flow rate control valve shown in FIG. It is a vertical sectional view of FIG. (A) is a side view of the valve body shown in FIG. 6, and (b) is a side view of the valve body in a state of being rotated 90 ° clockwise from the state of FIG. 6 (a). It is a comparison table which showed the relationship between the 1st to 3rd outlets and the 1st to 3rd openings in each phase of a valve body. It is a cross-sectional view of the flow rate control valve provided to explain the operating state of the flow rate control valve according to the present invention, the left side (I) of the column is the cross-sectional view taken along the line AA of FIG. 6, and the right side (II) is FIG. It is a cross-sectional view taken along the line BB. Further, the row (a) is a state in which only the first outlet is in communication, (b) is a state in which only the second outlet is in communication, (c) is a state in which all outlets are not in communication, and (d) is. Only the third outlet is in communication, (e) is the state in which the first and third outlets are in communication, and (f) is the state in which the second and third outlets are in communication. The operating state of the flow control valve shown in FIG. 9 is shown in an expanded view, in which (a) is a state in which only the first discharge port is in communication, and (b) is a state in which only the second discharge port is in communication. c) is a state in which all the discharge ports are not in communication, (d) is a state in which only the third discharge port is in communication, (e) is a state in which the first and third discharge ports are in communication, and (f) is a second. , It is a figure which shows the state which the 3rd discharge port communicates. It is a development view of the valve body which showed the other example of the embodiment of the flow rate control valve which concerns on this invention.

Hereinafter, embodiments of the flow control valve according to the present invention will be described with reference to the drawings. In the following embodiment, the flow control valve according to the present invention will be described as an example in which it is applied to a circulation system of cooling water for automobiles (hereinafter, simply abbreviated as "cooling water") similar to the conventional one.

(Construction of cooling water circulation circuit)
FIG. 1 shows a block diagram showing a configuration of a cooling water circulation circuit to which the flow control valve CV according to the present invention is applied. Further, FIG. 2 shows a block diagram showing a modified example of the circulation circuit shown in FIG.

The flow control valve CV is arranged on the side of the engine EG (specifically, a cylinder head (not shown)). As shown in FIG. 1, the flow control valve CV includes a radiator RD that cools the cooling water for cooling the engine EG, a bypass BP that bypasses the radiator RD and returns to the engine EG, and a bypass BP (not shown). It is arranged between a heater HT, which is a heating heat exchanger that exchanges heat to create hot air for an air conditioner.

Here, the reference numeral WP in the figure is a water pump used for circulation of cooling water. Further, the reference numeral WT is a water temperature sensor used for driving and controlling the flow rate control valve CV, and the reference numeral CU is a control means for driving and controlling the flow rate control valve CV based on the detection result of the water temperature sensor WT. Further, the reference numeral TS is a valve that opens and closes in response to the cooling water temperature, and is a thermostat that provides constant circulation of cooling water when the flow control valve CV becomes inoperable.

Specifically, the cooling water discharged from the water pump WP is guided to the flow rate control valve CV through the introduction passage L0. Then, the rotor RT in the flow rate control valve CV is driven and controlled by the control means CU based on the operating state of the engine EG such as the detection result by the water temperature sensor WT, so that the cooling water flows through the first to third pipes L1 to L3. It is distributed to the radiator RD, the bypass BP and the heater HT, respectively.

In this way, the flow control valve CV is applied as a so-called 1in-3Out type distribution device, distributes the cooling water flowing in from the introduction passage L0 to the first to third pipes L1 to L3, and at the time of the distribution. Control the flow rate of cooling water. On the other hand, when the flow control valve CV becomes inoperable due to, for example, an electrical failure, the thermostat TS is opened so that the cooling water guided from the introduction passage L0 directly passes through the return passage DL. It is directly returned to the engine EG side via the engine and is used for constant circulation. Further, depending on the detection result of the water temperature sensor WT, the cooling water flowing through the thermostat TS is supplied to the radiator RD through the bypass passage BL shown by the broken line in FIG. 1 to suppress the overheating of the engine EG.

The direct return passage DL and the thermostat TS are not essential configurations for the flow control valve CV, and may be omitted as shown in FIG. In this case, for example, by configuring a circuit that directly returns to the engine EG side without passing through the flow control valve CV, it is possible to cope with the inoperability of the flow control valve CV. Further, as shown in the figure, the water temperature sensor WT is not indispensable for the drive control of the flow rate control valve CV, and the flow rate control valve CV can be driven and controlled by means other than the water temperature detection by the water temperature sensor WT. It is possible.

FIG. 3 shows a block diagram showing another configuration of the cooling water circulation circuit to which the flow control valve CV according to the present invention is applied.

In addition to the types shown in FIGS. 1 and 2, the flow control valve CV is arranged immediately before the water pump WP, for example, as shown in FIG. 3, and can be applied as a so-called 3-in-1out type collective device. .. That is, when used as such an collecting device, the flow control valve CV collects the cooling water flowing in from the first to third pipes L1 to L3, returns the cooling water to the engine EG side through the discharge passage L4, and at the time of the gathering. Control the flow rate of the cooling water.

(Structure of flow control valve)
FIG. 4 shows an exploded perspective view of the flow control valve according to the present invention. Further, FIG. 5 shows a perspective view of the flow control valve shown in FIG. 4 in an assembled state. In the description of this figure, the direction parallel to the central axis Z of the drive shaft 2 is the "axial direction", the direction orthogonal to the central axis Z of the drive shaft 2 is the "radial direction", and the central axis Z of the drive shaft 2 is The surrounding direction will be described as "circumferential direction". Further, the "axial direction" will be described with the upper side in FIG. 4 as the "one end side" and the lower side as the "other end side".

As shown in FIG. 4, the flow control valve CV is housed in a tubular valve body 3 rotatably supported in the housing 1 via a drive shaft 2 and a housing 1, and rotationally drives the valve body 3. It has an electric motor 4 and a deceleration mechanism 5 housed in a housing 1 that decelerates and transmits the rotation of the electric motor 4.

The housing 1 is formed in two portions in the axial direction, and is provided so as to close the first housing 11 accommodating the valve body 3 and the electric motor 4 and the opening on one end side of the first housing 11, and the deceleration mechanism 5 is provided. It is composed of a second housing 12 for accommodating the above. The first housing 11 and the second housing 12 are each molded by casting with an aluminum alloy material, and are fixed by fixing means (not shown), for example, a plurality of bolts.

In the present embodiment, the first housing 11 and the second housing 12 are exemplified by those manufactured of an aluminum alloy material, but in addition to this, synthetic resins having heat resistance and chemical resistance, for example, engineering plastics, are exemplified. It may be produced by a polyphenylene sulfide resin (PPS resin) which is a kind of the above.

The first housing 11 is attached in parallel to the hollow cylindrical valve body accommodating portion 111 accommodating the valve body 3 and the valve body accommodating portion 111, and is a hollow cylindrical motor accommodating the motor body 41 of the electric motor 4. It has an accommodating portion 112 and. Then, the first housing 11 is fixed to a cylinder block (not shown) via a flange portion 114 (described later) by a fixing means (for example, a plurality of bolts) (not shown).

One end side of the valve body accommodating portion 111 in the axial direction is closed by the end wall 113, and the other end side is formed with an opening. A flange portion 114 for attaching the first housing 11 to a cylinder block (not shown) is extended on the outer peripheral side of the other end portion in the axial direction of the valve body accommodating portion 111. Further, on the end wall 113 of the valve body accommodating portion 111, a covered cylindrical boss portion 115 is formed so as to project toward the second housing 12. A shaft through hole 116 through which the drive shaft 2 penetrates is formed through the end wall of the boss portion 115. Further, on the end wall 113 of the valve body accommodating portion 111, a pair of flat plate-shaped bearing portions 117, 117 that pivotally support the intermediate shaft 50 of the deceleration mechanism 5, which will be described later, at both end portions in the radial direction (longitudinal direction). Is erected. Bearing holes 117a and 117a that rotatably support each end of the intermediate shaft 50 are formed through the pair of bearing portions 117 and 117, respectively.

The second housing 12 has a concave vertical cross-sectional shape that opens so as to cover both the valve body accommodating portion 111 and the motor accommodating portion 112 with the other end side in the axial direction facing the first housing 11 straddling the valve body accommodating portion 111 and the motor accommodating portion 112. Has been done. Then, the deceleration mechanism accommodating portion 121 accommodating the deceleration mechanism 5 is formed by the concave internal space.

In the electric motor 4, the motor body 41 is housed in the motor accommodating portion 112 so that the output shaft 42 faces the second housing 12 side. Then, the electric motor 4 is fixed to the opening edge portion of the motor accommodating portion 112 via a flange portion 43 extending in the radial direction at the end portion of the motor main body 41 on the output shaft 42 side, which is not shown. For example, it is fixed by a plurality of bolts. The electric motor 4 is controlled by an in-vehicle electronic controller (not shown), and the valve body 3 is rotationally driven according to the operating state of the vehicle to appropriately distribute the cooling water to the radiator RD and the like (see FIG. 1). It will be realized.

The reduction gear mechanism 5 is a drive mechanism composed of two sets of staggered gears, a first gear G1 and a second gear G2. The first gear G1 is provided coaxially with the output shaft 42 of the electric motor 4, and is arranged substantially orthogonally to the first screw gear WG1 that rotates integrally with the output shaft 42 and the output shaft 42 of the electric motor 4. It is composed of a first oblique gear HG1 which is fixed to the intermediate shaft 50 and meshes with the first screw gear WG1. The second gear G2 is fixed to the intermediate shaft 50 and is fixed to the second threaded gear WG2 that rotates integrally with the first oblique tooth gear HG1, and is fixed to the drive shaft 2 and meshes with the second threaded gear WG2. It is composed of a tooth gear HG2. In this way, the rotational driving force output from the output shaft 42 of the electric motor 4 is decelerated in two stages via the first gear G1 and the second gear G2 and transmitted to the valve body 3.

FIG. 6 shows a vertical cross-sectional view of FIG. In the description of this figure, the direction parallel to the central axis Z of the drive shaft 2 is the "axial direction", the direction orthogonal to the central axis Z of the drive shaft 2 is the "radial direction", and the central axis of the drive shaft 2 is The direction around Z will be described as "circumferential direction". Further, the "axial direction" will be described with the lower side in FIG. 4 as the "one end side" and the upper side as the "other end side".

As shown in FIG. 6, in the first housing 11, a valve body accommodating portion 111 having a substantially circular cross section for accommodating the valve body 3 is formed with an opening toward the other end side in the axial direction. On the other hand, in the end wall 113 of the valve body accommodating portion 111, that is, the end wall of the boss portion 115, a shaft through hole 116 through which the drive shaft 2 penetrates communicates the valve body accommodating portion 111 and the deceleration mechanism accommodating portion 121 described later. As such, it is formed along the axial direction. Further, in the first housing 11, a motor accommodating portion 112 having a substantially circular cross section for accommodating the motor main body 41 of the electric motor 4 is opened toward the second housing 12 side in a form adjacent to the valve body accommodating portion 111. It is formed (see FIG. 4).

The first housing 11 has a plurality of fixing means (for example, not shown) on the side portion of the cylinder head (not shown) via the flange portion 114 extending to the outer peripheral edge of the other end portion in the axial direction of the valve body accommodating portion 111. It is fixed by the bolt of. An introduction port E0 is formed on the inner peripheral side of the flange portion 114 as a main communication port for introducing cooling water from the cylinder block side by communicating with the inside of a cylinder block (not shown). That is, the introduction port E0 communicates with the opening on the other end side of the valve body accommodating portion 111, and the cooling water can be introduced into the valve body accommodating portion 111 via the introduction port E0.

Further, on the peripheral wall of the valve body accommodating portion 111, a plurality of through holes having a substantially circular cross section for communicating the outside and the valve body accommodating portion 111 are formed as first to third discharge ports E1 to E3. Corresponding first to third pipes L1 to L3 are connected to the respective discharge ports E1 to E3. The first discharge port E1 is connected to, for example, the radiator RD via the first pipe L1. The second discharge port E2 is connected to, for example, a bypass BP via the second pipe L2. The third discharge port E3 is connected to, for example, a heater HT via the third pipe L3.

Here, the first discharge port E1 and the second discharge port E2 are at different circumferential positions on the peripheral wall of the first housing 11, and the first discharge port E1 and the second discharge port E2 are in the axial direction. Arranged to polymerize. In particular, in the present embodiment, the center C1 of the first discharge port E1 and the center C2 of the second discharge port E2 are arranged so as to coincide with each other in the axial direction. Further, the third discharge port E3 is arranged in parallel in the axial direction with respect to the first discharge port E1 and the second discharge port E2.

It should be noted that the first discharge port E1 and the second discharge port E2 do not necessarily have to completely coincide with each other at the centers C1 and C2, and it is sufficient that at least a part of the first discharge port E1 and the second discharge port E2 are configured to be polymerizable in the axial direction. Therefore, even if the centers C1 and C2 of the first discharge port E1 and the second discharge port E2 are displaced in the axial direction, for example, the inner diameters of the first and second discharge ports E1 and E2 may be adjusted. 1. It is sufficient that the second discharge ports E1 and E2 and the first and second openings M1 and M2 of the valve body 3, which will be described later, can be polymerized.

Further, on the inner peripheral side of the first to third discharge ports E1 to E3, a sealing means for airtightly sealing between the respective discharge ports E1 to E3 and the valve body 3 is provided. This sealing means is made of metal that urges the cylindrical first to third sealing members S1 to S3 made of an elastic synthetic resin material and the first to third sealing members S1 to S3 toward the valve body 3. It is composed of first to third coil springs SP1 to SP3.

The first to third seal members S1 to S3 are housed and arranged on the inner peripheral side of the first to third discharge ports E1 to E3, and are provided so as to be movable back and forth toward the valve body 3 side, respectively. The first to third coil springs SP1 to SP3 are arranged between the first to third seal members S1 to S3 and the first to third pipes L1 to L3 with a predetermined set load, and the seal members S1 to S3, respectively. Is an urging member that urges the valve body 3 side.

The drive shaft 2 has a rod shape having a constant outer diameter, is arranged so as to pass through the shaft through hole 116 and straddle the valve body accommodating portion 111 and the deceleration mechanism accommodating portion 121, and is accommodated and held on the inner peripheral side of the boss portion 115. It is rotatably supported by the bearing B1. Further, the space between the drive shaft 2 and the shaft through hole 116 is airtightly sealed by the annular seal member 20. That is, the seal member 20 prevents the cooling water from flowing out to the second housing 12 side in the valve body accommodating portion 111 through the shaft through hole 116.

The valve body 3 has a covered cylindrical shape having a constant outer diameter, and is provided so that the opening on the other end side faces the introduction port E0 side, so that the cooling water is provided in the internal passage 118 formed on the inner peripheral side. It is designed to guide. The valve body 3 is press-fitted and fixed to the drive shaft 2 via a metal insert member 30 embedded in the inner peripheral side of one end in the axial direction, and the other end facing the introduction port E0 side is introduced. It is rotatably supported by a bearing B2 held on the inner peripheral side of the port E0.

7A and 7B show a side view of the valve body 3 shown in FIG. 6, and FIG. 7B is a side view of the valve body 3 in a state of being rotated 90 ° clockwise from the state of FIG. 7A. Shows. In the description of this figure, the direction parallel to the rotation axis Z of the valve body 3 is the "axial direction", the direction orthogonal to the rotation axis Z of the valve body 3 is the "radial direction", and the rotation axis Z of the valve body 3 is The surrounding direction will be described as "circumferential direction".

As shown in FIG. 7, the first to third openings M1 to M3 corresponding to the first to third outlets E1 to E3 of the first housing 11 are formed through the outer peripheral surface of the valve body 3, respectively. There is. Specifically, the first opening M1 and the second opening M2 are both formed as substantially circular holes, have different circumferential positions on the outer peripheral surface of the valve body 3, and are different from the first opening M1. The second opening M2 is arranged so as to overlap with each other in the axial direction. In particular, in the present embodiment, the center C1 of the first opening M1 and the center C2 of the second opening M2 are arranged so as to coincide with each other in the axial direction. Further, the third opening M3 is formed as an elongated hole extending in the circumferential direction, and is arranged in parallel with the first opening M1 and the second opening M2 in the axial direction. The first opening M1 and the second opening M2 do not necessarily have to coincide with each other at the centers C1 and C2, and it is sufficient that at least a part of the first opening M1 and the second opening M2 are formed so as to be polymerized in the axial direction.

From such a configuration, as shown in FIGS. 6 and 7, the valve body 3 is controlled to a position where at least a part of the first opening M1 and the first discharge port E1 overlaps (overlaps), so that the first piping Cooling water is distributed to L1. Similarly, by controlling the valve body 3 at a position where at least a part of the second opening M2 and the second discharge port E2 overlaps, the valve body 3 is connected to the second pipe L2, and the third opening M3 and the third discharge port are connected. By controlling the valve body 3 at a position where at least a part of E3 is polymerized, the cooling water is distributed to the third pipe L3. Then, with respect to the distribution of the cooling water, the polymerization area (overlapping condition) when the first to third openings M1 to M3 and the first to third outlets E1 to E3 are polymerized changes, so that the distribution is concerned. The flow rate of the cooling water changes.

FIG. 8 shows the relationship between the first to third outlets E1 to E3 and the first to third openings M1 to M3 at each rotation position (phase) of the valve body 3, that is, the first to third outlets E1 to E3. It is a comparison table showing whether the first to third openings M1 to M3 are in a communicating state or are in a non-communication state. In FIG. 8, the circles indicate that the first to third outlets E1 to E3 and the first to third openings M1 to M3 communicate with each other, and the crosses indicate the first to third outlets. It is shown that the outlets E1 to E3 and the first to third openings M1 to M3 are in a non-communication state, respectively.

That is, the first to third openings M1 to M3 are arranged so as to be in the communication state (first to sixth states) shown in FIG. 8 when the valve body 3 is controlled to a predetermined rotation position (phase). Has been done. Specifically, only the first discharge port E1 communicates in the first state, only the second discharge port E2 communicates in the second state, and the first to third discharge ports E1 to E3 communicate with each other in the third state. Everything is out of communication. Further, only the third discharge port E3 communicates in the fourth state, the first and third discharge ports E1 and E3 communicate with each other in the fifth state, and the second and third discharge ports E2 and E3 communicate with each other in the sixth state. It will be in the state of.

(Explanation of operation of flow control valve)
9A and 9B are cross-sectional views of the flow rate control valve CV used to explain the operating state of the flow rate control valve CV. The left side (I) of the parallel column is the cross-sectional view taken along the line AA of FIG. The sectional view taken along line BB of FIG. 6 is shown. Further, the row (a) is a state in which only the first discharge port E1 is in communication, (b) is a state in which only the second discharge port E2 is in communication, and (c) is a state in which all of the first to third discharge ports E1 to E3 are in communication. Non-communication state, (d) is a state in which only the third discharge port E3 is in communication, (e) is a state in which the first and third discharge ports E1 and E3 are in communication, and (f) is a state in which the second and third discharge ports are in communication. It shows a state in which the exits E2 and E3 communicate with each other.

Further, FIG. 10 shows the operating state of the flow control valve CV shown in FIG. 9 as a developed view, in which (a) is a state in which only the first discharge port E1 communicates, and (b) is the second discharge port E2. (C) is a state in which all of the first to third outlets E1 to E3 are not in communication, (d) is a state in which only the third outlet E3 is in communication, and (e) is the first. , The state in which the third discharge ports E1 and E3 communicate with each other, and (f) shows the state in which the second and third discharge ports E2 and E3 communicate with each other. In the explanation of this figure, the first to third openings M1 to M3 of the valve body 3 are shown by broken lines, while the first to third outlets E1 to E3 of the first housing 11 are hatched. By displaying and displaying the state in which both E1 to E3 and M1 to M3 are overlapped and communicated with each other, the first to third outlets E1 to E3 and the first to third openings M1 to M3 are displayed for convenience. Relative identification shall be attempted.

The flow control valve CV is driven and controlled by a control current from an electronic controller (not shown) that is calculated and output based on the operating state of the vehicle, so that the first to first flow control valves CV are controlled according to the operating state of the vehicle. 3 The valve body 3 is controlled so that the relative phases of the first to third openings M1 to M3 with respect to the discharge ports E1 to E3 are the first to sixth phases shown in FIGS. 9 and 10. ..

In the first phase shown in FIGS. 9 (a) and 10 (a), only the first opening M1 of the first to third openings M1 to M3 is in a communicating state, and the second and third openings M2 M3 is in a non-communication state. As a result, in the first phase, the cooling water is supplied only to the radiator RD from the first discharge port E1 through the first pipe L1, and the supply amount is based on the polymerization amount of the first discharge port E1 and the first opening M1. Will change.

After the first phase, in the second phase shown in FIGS. 9 (b) and 10 (b), only the second opening M2 of the first to third openings M1 to M3 is in a communicating state, and the first and third openings are in communication. The third openings M1 and M3 are in a non-communication state. As a result, in the second phase, the cooling water is supplied only to the bypass BP from the second discharge port E2 through the second pipe L2, and the supply amount is based on the polymerization amount of the second discharge port E2 and the second opening M2. Will change.

After the second phase, in the third phase shown in FIGS. 9 (c) and 10 (c), all of the first to third openings M1 to M3 refer to the first to third outlets E1 to E3. It becomes a non-communication state. As a result, in the third phase, the cooling water is not supplied to any of the radiator RD, the bypass BP, and the heater HT.

After the third phase, in the fourth phase shown in FIGS. 9 (d) and 10 (d), only the third opening M3 out of the first to third openings M1 to M3 is in a communicating state, and the first and third openings are in communication. The second openings M1 and M2 are in a non-communication state. As a result, in the fourth phase, cooling water is supplied only to the heater HT from the third discharge port E3 through the third pipe L3, and the cooling water is supplied based on the amount of polymerization between the third discharge port E3 and the third opening M3. The amount of supply will change.

After the fourth phase, in the fifth phase shown in FIGS. 9 (e) and 10 (e), only the second opening M2 of the first to third openings M1 to M3 is in a non-communication state, and the first phase. , The third openings M1 and M3 are in a communicating state. As a result, in the fifth phase, cooling water is supplied from the first and third discharge ports E1 and E3 to the radiator RD and the heater HT through the first and third pipes L1 and L3, and the first and third discharge ports are supplied. The supply amount changes based on the polymerization amount of E1 and E3 and the first and third openings M1 and M3.

After the fifth phase, in the sixth phase shown in FIGS. 9 (f) and 10 (f), only the first opening M1 of the first to third openings M1 to M3 is in a non-communication state, and the second phase. , The third openings M2 and M3 are in a communicating state. As a result, in the sixth phase, cooling water is supplied from the second and third discharge ports E2 and E3 to the bypass BP and the heater HT through the second and third pipes L2 and L3, and the second and third discharge ports are supplied. The supply amount changes based on the polymerization amount of E2 and E3 and the second and third openings M2 and M3.

As described above, in the flow rate control valve CV according to the present embodiment, the third outlet E3 and the third opening M3 are not always in communication in the first to third phases, and the first opening M1 and the first opening M1 and the first opening M3 are not in communication with each other. 2 The communication state of the opening M2 changes. That is, when the heater HT is not used, such as on a day when the temperature is relatively high, the valve body 3 is in the so-called "warm-up mode" as the first state of the present invention, which comprises the first to third phases on one side in the circumferential direction. Controlled, the third outlet E3 and the third opening M3 are always out of communication, and only the communication state of the first and second openings M1 and M2 changes.

The third phase in which the first to third outlets E1 to E3 and the first to third openings M1 to M3 are all non-communication corresponds to the third state of the present invention. The state is configured to be located between the first state and the second state described later.

On the other hand, in the 4th to 6th phases, the third outlet E3 and the third opening M3 are always in communication, and the communication state of the first opening M1 and the second opening M2 changes. That is, when the heater HT is used on a day when the temperature is relatively low, the valve body 3 is in the so-called "cold air mode" as the second state of the present invention, which comprises the fourth to sixth phases on the other side in the circumferential direction. Controlled, the communication state of the first and second openings M1 and M2 changes in a state where the third discharge port E3 and the third opening M3 are always in communication.

(Action and effect of this embodiment)
In the conventional flow rate control valve, the first opening, the second opening, and the third opening are arranged in series in the rotation axis direction of the valve body. Therefore, there is a problem that the valve body becomes large in the direction of the rotation axis.

Further, in the conventional flow rate control valve, two first openings M1 are provided for the first discharge port E1 and two second openings M2 are provided for the second discharge port E2. .. Therefore, a larger surface area is required in the valve body in order to secure the two first and second openings M1 and M2, respectively, and there is also a problem that the valve body becomes large in the radial direction.

On the other hand, the flow rate control valve CV according to the present embodiment can solve the problem of the conventional flow rate control valve by achieving the following effects.

That is, the flow control valve CV is provided in the valve body accommodating portion 111, and has an introduction port E0 as a main communication port for introducing or discharging a fluid (introduced in the present embodiment), and the valve body accommodating portion 111 in the radial direction. With the housing 1 having the first to third discharge ports E1 to E3 as the first to third communication ports for discharging or introducing the fluid in the valve body accommodating portion 111 (draining in the present embodiment). With the valve body 3 having the first to third openings M1 to M3 which are rotatably supported in the housing 1 and whose superposition state with the first to third discharge ports E1 to E3 changes according to the rotation position thereof. The electric motor 4 as an actuator for controlling the rotational position of the valve body 3 is provided, and the first opening M1 and the second opening M2 are located at least at different circumferential positions on the outer peripheral surface of the valve body 3. A part of the valve body 3 is formed so as to overlap in the rotation axis direction, and the third opening M3 is formed in parallel with the first opening M1 in the rotation axis direction of the valve body 3. The first state in which the discharge port E3 and the third opening M3 are always in communication and the communication state of the first opening M1 and the second opening M2 changes, and the third communication port E3 and the third opening M3 It has a second state in which communication is always non-communication and the communication state of the first opening M1 and the second opening M2 changes.

As described above, in the flow control valve CV according to the present embodiment, at least a part of the first opening M1 and the second opening M2 rotate at different circumferential positions on the outer peripheral surface of the valve body 3. It is formed so as to polymerize in the axial direction. Therefore, it is possible to shorten the axial dimension of the valve body 3 as compared with the conventional flow rate control valve in which the first to third openings M1 to M3 are separated from each other without overlapping in the axial direction. , It is possible to suppress the increase in size of the valve body 3 in the axial direction.

Further, in the present embodiment, one first opening M1 is provided for each first discharge port E1, and one second opening M2 is provided for each second discharge port E2. Therefore, the number of openings on the outer peripheral surface in the circumferential direction of the valve body can be reduced as compared with the conventional flow rate control valve in which two or more openings are provided for each discharge port. As a result, in the flow control valve CV, the surface area of the valve body 3 can be reduced by the amount of the reduced opening, and the diameter of the valve body 3 can be reduced, resulting in a larger size of the valve body 3. It can be effectively suppressed.

Further, the flow rate control valve CV has a third state in which the first to third discharge ports E1 to E3 and the first to third openings M1 to M3 are all non-communication.

As described above, in the present embodiment, in the third state, the first to third outlets E1 to E3 and the first to third openings M1 to M3 are all configured to be non-communication. As a result, by setting the third state when the cold machine is started, the engine EG can be warmed up at an early stage, and the amount of harmful substances in the exhaust gas discharged from the engine EG can be reduced.

Further, in the flow control valve CV, the third state is configured between the first state and the second state in the rotation direction of the valve body 3.

As described above, in the present embodiment, the third state is configured between the first state and the second state in the rotation direction of the valve body 3. As a result, when the engine EG is started, it is possible to shift to the first state or the second state with the third state (third phase) as the base point. As a result, the transition from the third state to the first state or the second state is smoother and in a shorter time than in the case where the third state is configured to be located at the end in the valve body rotation direction. It can be done with good responsiveness.

Further, in the flow control valve CV, the first discharge port E1 is connected to the radiator RD, the second discharge port E2 is connected to the bypass BP that bypasses the radiator RD, and the third discharge port E3 is connected to the heater HT. It is connected.

As described above, in the present embodiment, in particular, since the third discharge port E3 is connected to the heater HT, the first to third phases on one side in the circumferential direction of the valve body 3 are in the warm air mode, and the fourth on the other side. The sixth phase is the cold air mode. In other words, the rotation direction of the valve body 3 can be divided into two, and one side can be set to the warm air mode and the other side can be set to the cold air mode. As a result, the controllability of the valve body 3 can be improved.

The present invention is not limited to the configuration of the above-described embodiment, and can be freely changed according to the specifications of the steering device to be applied and the like as long as the mode can exhibit the effects of the present invention.

In particular, in the above embodiment, as an example of the application of the flow control valve CV, the application of the cooling water to the circulation system has been exemplified, but the flow control valve CV is not limited to the cooling water but also various types such as lubricating oil. It goes without saying that it is applicable to fluids.

Further, in the present embodiment, the valve body 3 provided with the three openings M1 to M3 of the first to third openings is exemplified, but the number of the openings may be 3 or more, and the first The first to third openings are not limited to M1 to M3. In other words, for example, as shown in FIG. 11, the fourth opening M4 may be provided in the circumferential direction of the valve body 3, and the fifth opening M5 may be provided in the axial direction of the valve body 3. In this case, the first and second openings M1, M2 to the first, second and fourth openings M1, M2 and M4 correspond to the first opening system G1 of the present invention, and the third opening. M3 to the third and fifth openings M3 and M5 correspond to the second opening system G2 of the present invention.

In such a configuration, the flow control valve is provided in the valve body accommodating portion 111, and has an introduction port E0 as a main communication port for introducing or discharging a fluid (introduced in the present embodiment) and a valve body accommodating portion 111. It has first to third discharge ports E1 to E3 as first to third communication ports for discharging or introducing (draining in the present embodiment) the fluid in the valve body accommodating portion 111. Three or more openings (for example, as shown in FIG. 11) that are rotatably supported in the housing 1 and the overlapping state of the first to third outlets E1 to E3 changes according to the rotation position thereof. The valve body 3 having the first to fifth openings M1 to M5) and the electric motor 4 as an actuator for controlling the rotation position of the valve body 3 are provided, and at least two of the three or more openings are provided. The first opening system G1 including the first opening M1 and the second opening M2, which are openings, is at least a part of the first and first openings at different circumferential positions on the outer peripheral surface of the valve body 3. The two openings M1 and M2 are formed so as to overlap each other in the rotation axis direction of the valve body 3, and the first and second openings M1 and 2 belonging to the first opening system G1 among the three or more openings are formed. The second opening system G2 composed of the third opening M3 to the third and fifth openings M1 and M5, which are one or more openings different from M2, rotates the valve body 3 with respect to the first opening system G1. The first and second outlets E1 and E2, which are formed in parallel in the axial direction and overlap with the first opening system G1, are in a state where the first opening system G1 is not communicated with each other in the rotation direction of the valve body 3 (the first). It suffices if they are arranged so that the communication state changes with the third state (third state consisting of three phases) interposed therebetween. As a result, the same effect as that of the embodiment can be obtained.

As the flow rate control valve based on the embodiment described above, for example, the one described below can be considered.

That is, in one aspect thereof, the flow control valve is provided in the valve body accommodating portion and communicates with the main communication port for introducing or discharging the fluid from the valve body accommodating portion in the radial direction to accommodate the valve body. A housing having first to third communication ports for discharging or introducing fluid in the unit, and rotatably supported in the housing, the overlapping state of each communication port changes according to the rotation position. A valve body having the first to third openings and an actuator for controlling the rotation position of the valve body are provided, and the first opening and the second opening are different on the outer peripheral surface of the valve body. At least a part of the peripheral position is formed so as to overlap in the rotation axis direction of the valve body, and the third opening is parallel to the first opening in the rotation axis direction of the valve body. The first state in which the third communication port and the third opening are constantly communicated with each other and the communication states of the first opening and the second opening change, and the third communication port and the above. It has a second state in which the third opening is always non-communication and the communication state of the first opening and the second opening changes.

In a preferred embodiment of the flow control valve, the first to third communication ports and the first to third openings are all non-communication with a third state.

In another preferred embodiment, in any of the aspects of the flow control valve, the third state is configured between the first state and the second state in the direction of rotation of the valve body.

In yet another preferred embodiment, in any of the aspects of the flow control valve, the first communication port is connected to a radiator and the second communication port is connected to a bypass bypassing the radiator, the third communication port. The mouth is connected to the heater.

Further, from another viewpoint, in one aspect thereof, the control valve is provided in the valve body accommodating portion and communicates with the main communication port for introducing or discharging the fluid from the radial direction. A state in which a housing having three or more communication ports for discharging or introducing fluid in the valve body accommodating portion and the three or more communication ports rotatably supported in the housing and having three or more communication ports depending on the rotation position thereof are overlapped with each other. A first opening system comprising at least two openings out of the three or more openings comprising a valve body having three or more openings in which the valve body changes and an actuator for controlling the rotation position of the valve body. At least a part of the openings are formed so as to overlap each other in the rotation axis direction of the valve body at different circumferential positions on the outer peripheral surface of the valve body, and the first of the three or more openings. A second opening system composed of one or more openings different from the openings belonging to the one opening system is formed in parallel with the first opening system in the rotation axis direction of the valve body, and the first opening system is formed. Each communication port overlapping with the above is arranged so that the communication state changes in the rotation direction of the valve body with the state in which the first opening system is non-communication.

1 ... Housing, 10 ... Introduction port (main communication port), 11 ... 1st housing, 111 ... Valve body accommodating part, 12 ... 2nd housing, E1 to E3 ... 1st to 3rd discharge ports (communication port) 3 ... Valve body, M1 to M3 ... 1st to 3rd openings (openings), 4 ... Electric motor (actuator)

Claims (3)

The first to third communication ports provided in the valve body accommodating portion for introducing or discharging the fluid and communicating with the valve body accommodating portion in the radial direction to discharge or introduce the fluid in the valve body accommodating portion. A housing with a communication port and
A valve body that is rotatably supported in the housing and has first to third openings whose overlapping state with each communication port changes according to the rotation position.
A motor that controls the rotational position of the valve body and
Equipped with
The first communication port is connected to the radiator and
The second communication port is connected to a bypass that bypasses the radiator.
The third communication port is connected to the heater and is connected to the heater.
The housing is provided on the radial outer side of the valve body so as to be adjacent to the valve body accommodating portion, and has a hollow cylindrical motor accommodating portion for accommodating the motor.
The motor is arranged so that the output shaft of the motor is substantially parallel to the rotation axis of the valve body .
The first opening and the second opening are formed at different circumferential positions on the outer peripheral surface of the valve body so that at least a part thereof overlaps with each other in the rotation axis direction of the valve body.
The third opening is formed in parallel with the first opening in the rotation axis direction of the valve body.
The first state in which the third communication port and the third opening are always in communication and the communication state of the first opening and the second opening changes.
A second state in which the third communication port and the third opening are always non-communication and the communication state of the first opening and the second opening changes.
Have,
A flow control valve characterized in that the motor accommodating portion is located at a position where the first communication port and the second communication port overlap in a direction orthogonal to the rotation axis . The flow rate control valve according to claim 1, wherein the first to third communication ports and the first to third openings all have a third state of non-communication. The flow rate control valve according to claim 2, wherein the third state is configured between the first state and the second state in the rotation direction of the valve body.

Images