FLOW CONTROL VALVE

Abstract

A flow control valve (CV) that includes: a housing (1) which has: a main communication port (10) for introducing or discharging fluid, provided on a valve body receiving part (13) which is designed in a hollow shape; and a plurality of communication ports (E1-E3), each of which communicates with the valve body receiving part (13) from a radial direction, and is configured to supply or discharge fluid into the valve body receiving part (13); a valve body (3) rotatably mounted in the housing (1) and has a plurality of opening sections (M1-M3) whose overlapping states with the respective communication ports (E1-E3) are changed according to the rotational position of the valve body (3); and Sealing elements (S1-S3) arranged between the housing (1) and an outer circumferential surface of the valve body (3) in a radial direction with reference to a rotational axis of the valve body (3), Division lines (P1, P2, P3) provided on the outer circumferential surface of the valve body (3), wherein at least one of the division lines (P1, P2, P3) is provided at positions on the outer circumferential surface of the valve body (3) that is not facing the sealing elements (S1-S3) at any point in any area of ​​the valve body (3) during actuation.

Description

[0001] The present invention relates to a flow control valve, used for, for example, flow control of coolant for a vehicle.

[0002] For example, a flow control valve of the state of the art, used for flow control of coolant for a vehicle, was known, for example, a flow control valve described in JP 2013- 249 904 A.

[0003] This flow control valve is a so-called rotary type valve, which performs flow control according to a rotational position (phase) of a rotor, which is an essentially cylindrical valve body, and has a structure in which the valve is open when the opening positions of a housing and the opening positions of the rotor overlap, and the valve is closed by pressing sealing elements against the outer circumferential wall, which is a non-opening section of the rotor, by the pressure force of elastic elements that are elastically positioned in the opening positions of the housing.

[0004] In a case where cooling water is to be distributed to multiple auxiliary units via the flow control valve, that is, in a case where multiple opening sections of the rotor are formed circumferentially, and these opening sections are formed simultaneously with the casting of the valve body, it becomes necessary to divide the mold into multiple parts (for example, three parts), depending on the number and position of the opening sections. In this case, due to the aforementioned division, unevenness is formed by so-called parting lines at a circumferential position, corresponding to the connection surfaces of the mold, on the outer circumferential wall of the rotor.

[0005] If the unevenness is formed, comparable to the flow control valve in the prior art, in a case where a structure is adopted in which the sealing element is pressed against the outer circumferential wall of the rotor for sealing, and the valve is closed, there is a concern that the sealing surface of the sealing element is damaged by sliding the sealing element against the unevenness.

[0006] Furthermore, publication JP 2000-130 610 A discloses a control valve with a rotatably mounted valve body, wherein a grade is arranged in a recess.

[0007] The present invention was developed in consideration of such a technical problem. One object of the present invention is to provide a flow control valve capable of protecting the sealing surface of a sealing element from damage. This object is achieved according to the invention by a flow control valve having the features of independent claim 1. Preferred embodiments are set forth in the dependent claims.

[0008] A flow control valve has sealing elements arranged radially between a housing and a valve body, which is rotatably mounted within the housing. The sealing elements hermetically seal the space radially between the housing and the valve body by sliding against the outer circumferential surface of the valve body. The valve is characterized in that the flow of fluid flowing from or into the inner circumferential surface of the valve body is modified by changing the overlap states between communication ports that communicate the inner and outer surfaces of the housing and the respective opening sections that communicate the inner and outer surfaces of the valve body. Dividing lines are provided at positions that do not slide against the sealing elements in the valve body.

[0009] Additionally, with regard to the provision of each of the division lines at positions that do not slide against the sealing elements in the valve body, various types of aspects are included in which, in addition to the simple provision of the division lines at non-sealing areas (an unused area) where the sealing elements do not slide against the sliding contact surfaces of the valve body, for example, level difference parts which are radially lower inwards than the contact surfaces are provided in advance at the sliding contact surfaces of the valve body against which the sealing elements slide, within areas in which at least the communication ports and the respective opening sections overlap, in the circumferential area of ​​the valve body, and the division lines are provided in the respective level difference parts.

[0010] According to the present invention, it is possible to avoid a deficiency in which the sealing surfaces of the sealing elements slide against the parting line, and thereby damage to the sealing surfaces of the sealing elements can be suppressed.

[0011] At this point, in a case where the parting lines are provided on the unused area, which is the non-sealing area, machining is not necessary even if the parting lines are formed, and it is an advantage that the valve body is excellently manufactured.

[0012] On the other hand, as mentioned above, in a case where the level difference parts are pre-formed on the sealing-sliding contact surfaces, and the division lines are provided in the respective level difference parts, it becomes possible to reduce the non-sealing area, and there is an advantage that the size of the valve body can be reduced. Description of the drawings Fig. Figure 1 is a circulation diagram of coolant, used to explain a flow control valve according to the present invention when applied to a circulating coolant system of a vehicle. Fig. Figure 2 is a circuit diagram for cooling water, which shows another application example for the flow control valve according to the present invention. Fig. Figure 3 is a perspective exploded view of the flow control valve according to a first embodiment of the present invention. Fig. Figure 4 is a top view of the flow control valve, shown in Fig. 3 Fig. 5 is a sectional view along a line AA of Fig. 4. Fig. 6(a) is a main part view, enlarged from Fig. 5, and Fig. 6(b) is a sectional view along a line BB of Fig. 6(a). Fig. Figure 7 is a side view of the flow control valve, shown in Fig. 4. Fig. 8 is a section view along a line CC of Fig. 7. Fig. Figure 9 is a longitudinal sectional view of a safety valve, shown in Fig. 3, and Fig. 9(a) is a drawing showing a valve closed state, and Fig. Figure 9(b) is a drawing showing a valve open state. Fig. 10(a) to Fig. Figure 10(d) shows perspective views of a valve body, as shown in Fig. 3, viewed from different perspectives. Fig. 11(a) is a drawing which is oriented from an arrow D direction of Fig. 10(a) is considered, and Fig. 11(b) is a sectional view along a line EE of Fig. 10(a). Fig. 12(a) to Fig. 12(c) are side views of the valve body, and Fig. 12(a) is a drawing showing a first division line, Fig. 12(b) is a drawing showing a second dividing line, and Fig. 12(c) is a drawing showing a third dividing line. Fig. Figure 13 is a perspective view of a reduction gear mechanism, shown in Fig. 3. Fig. Figure 14 is a top view of the reduction gear mechanism, shown in Fig. 13. Fig. 15 is a sectional view along a line FF of Fig. 14. Fig. 16(a) to Fig. Figure 16(d) shows a development view of a valve receiving part to explain an operating state of the flow control valve according to the present invention. Fig. Figure 16(a) shows a state in which all drain connections are in a non-communication state, Fig. 16(b) shows a state in which only one first drain connection is in a communication state, and Fig. Figure 16(c) shows a state in which the first and second drain connections are in communication states, and Fig. Figure 16(d) shows a state in which all of the drain connections are in communication states. Fig. 17(a) and Fig. Figure 17(b) shows main part sectional views of the flow control valve in the first embodiment of the present invention. Fig. Figure 17(a) shows a state before a first sealing element passes through a first level difference part, and Fig. Figure 17(b) shows a state when the first sealing element passes through the first level difference part. Fig. Figure 18 is a perspective view of a valve body, which is another example of the valve body of Fig. 3 shows. Fig. 19(a) and Fig. Figure 19(b) shows main part sectional views of the flow control valve in a second embodiment of the present invention. Fig. Figure 19(a) shows a state before a third sealing element passes through a third level difference part, and Fig. Figure 19(b) shows a state when the third sealing element passes through the third level difference part. Mode for carrying out the invention

[0013] Each embodiment of a flow control valve according to the present invention will now be explained with reference to the drawings. Additionally, in each of the following embodiments, the flow control valve of the present invention, applied to a conventional circulating system of coolant for a vehicle (hereinafter simply referred to as "coolant"), which is the same as a conventional one, will be referred to as an example. [First embodiment]

[0014] Fig. 1 to Fig. Figure 18 shows a first embodiment of the flow control valve according to the present invention. First, a cooling water circulation circuit in which the flow control valve CV is used is described. As in Fig. As shown in Figure 1, the flow control valve CV is located on a side part of the engine EG (specifically a cylinder head, which is not shown in the drawings) and is positioned between the engine EG and a heater-heat exchanger HT (an EGR or EC), an oil cooler OC, and a radiator RD. Additionally, the flow control valve CV distributes the cooling water, which is fed into the flow control valve CV through an inlet passage L0 by being pressurized by a water pump WP, to the heater-heat exchanger HT, the oil cooler OC, and the radiator RD through their respective first to third lines L1 to L3, and controls the flow rate of each of these first to third lines. At this point, the cooling water that has been fed into the heater-heat exchanger HT, after having entered the EGR cooler EC, has circulated to the engine EG.

[0015] Additionally, the flow control valve CV is provided with a bypass passage BL to supply the cooling water directly to a throttle chamber TC by bypassing the inlet passage L0. Through the bypass passage BL, the cooling water supplied by the engine EG can always be fed to the throttle chamber TC. The cooling water supplied to the throttle chamber TC, similar to the cooling water supplied to the heater core HT, is introduced into the EGR cooler EC, following the coolant circulating through the EGR cooler EC in the engine EG. A symbol WT in Fig. 1 denotes a water temperature sensor.

[0016] Additionally, regarding the arrangement of the flow control valve CV, this is not limited to the arrangement immediately after the motor EG, and, for example, as in Fig. As shown in Figure 2, the flow control valve CV can be arranged directly upstream of the motor EG, and the arrangement can preferably be modified according to the specifications of an article in which the flow control valve CV is mounted. Regarding the distribution of the cooling water to the throttle chamber TC, as described below, this is not applicable to an article for controlling the flow of the cooling water. As shown in Figure 2, the flow control valve CV can be arranged directly upstream of the motor EG, and the arrangement can preferably be modified according to the specifications of an article in which the flow control valve CV is mounted. Fig. 2 shown, as well as the presence or absence of the bypass BL, it is therefore preferably modified according to a specification of an item on which the flow control valve CV is mounted.

[0017] Next, a specific configuration of the CV flow control valve will be explained. As in Fig. 3 and Fig. As shown in Figure 15, the flow control valve CV is mainly configured from a housing 1, formed from a first housing 11, which accommodates the valve body 3 and electric motor 4 (hereinafter referred to as such), and a second housing 12, which accommodates the reduction gear mechanism 5 (hereinafter referred to as such), a rotary shaft 2, which is inserted into and positioned in an end wall 11b of the first housing 11, end wall 11b, which defines the first housing 11 and the second housing 12, and which is rotatably mounted by a bearing B1 held by the end wall 11b, the substantially cylindrical valve body 3, which is fixed to one end part of the rotary shaft 2 and which is rotatably mounted in the first housing 11, an electric motor 4, which is arranged parallel to the valve body 3 in the first housing 11 and which is used to actuate the valve body 2, and a Reduction gear mechanism 5,which is placed between a motor output shaft 4c of the electric motor 4 and the rotating shaft 2, and which reduces the speed of rotation of the electric motor 4 and transmits it.

[0018] The first housing 11 is a housing cast from aluminum alloy material. The first housing 11 is provided with a substantially cylindrical valve receiving part 13 opening at one end in an axial direction, the valve receiving part 13 being positioned close to the other end in a lateral direction and accommodating the valve body 3, and with a substantially cylindrical motor receiving part 14 opening at the other end in the axial direction, the motor receiving part 14 being positioned close to the other end in the lateral direction, so that it is adjacent to the valve body receiving part 13 and accommodating the electric motor 4.The first housing 11 is fixed to a side part of the engine, not shown in the drawings, by bolts, not shown in the drawings, by a first flange section 11a extending from the outer circumferential region of the opening at an end face of the valve body receiving part 13. Additionally, at the time of attachment of the first housing 11, a circumferential sealing element SL1 is inserted between the first flange section 11a of the first housing 11 and the side part of the engine, thereby hermetically sealing the interior of the valve body receiving part 13.

[0019] One end-side opening of the valve body receiving part 13 is configured as an inlet port 10, serving as a main communication port. This port introduces cooling water from the interior of the engine (not shown in the drawings) through communication with the engine's interior. The cooling water is introduced through the inlet port 10 into an inner circumferential side passage 17 and an outer circumferential side passage 18, respectively, formed on the inner and outer circumferential sides of the valve body 3. Additionally, a plurality of essentially cylindrical first to third outlet ports E1 to E3, serving as communication ports, each connect the first to third lines L1 to L3. These ports extend radially through the circumferential wall of the valve body receiving part 13 at predetermined positions.In the first to third outlet ports E1 to E3, the first outlet port E1, which has a medium diameter and communicates with the heater heat exchanger HT, and the second outlet port E3, which has a small diameter and communicates with the oil cooler OC, are arranged to overlap each other in the axial direction of the valve body receiving part 13 (they are radially opposite each other), and the second outlet port E2, which has a small diameter and communicates with the oil cooler OC, and the third outlet port E3, which has a large diameter and communicates with the radiator RD, are arranged parallel to each other in the axial direction of the valve body receiving part 13. The first and second outlet ports E1 and E2 are located close to the inlet port 10, and the third outlet port E3 is located close to the end wall 11b.

[0020] Here, as in Fig. 5 and Fig. As shown in Figure 6, the inner side ends of the respective first to third outlet ports E1 to E3 are provided with insert sections 19, which serve as sliding guides for the first to third sealing elements S1 to S3 mentioned later. By casting aluminum alloy material, the insert sections 19 are integrally formed with the first housing 11 at the respective inner side ends of the outlet ports E1 to E3, such that the inner side end surfaces of the insert sections 19 become essentially flat, i.e., the protrusion of each of the sealing elements S1 to S3 from the respective inner side ends of the outlet ports E1 to E3 is suppressed. With this configuration, through the insert sections 19, it is possible to suppress deformation of each of the sealing elements S1 to S3, and abrasion of each of the sealing elements S1 to S3 due to the deformation of each of the sealing elements S1 to S3 is suppressed.

[0021] The inner circumferential sides of the first to third outlet ports E1 to E3 are provided with sealing devices which hermetically seal the respective spaces between outlet port E1 and valve body 3, outlet port E2 and valve body 3, and between outlet port E3 and valve body 3, at the time of closing the first to the third outlet ports E1 to E3. These sealing devices are configured from the essentially cylindrical sealing elements S1 to S3, which are mounted so that they are movable forwards and backwards in the respective inner end faces of the outlet ports E1 to E3, and which seal the respective spaces between the outlet port E1 and the valve body 3, the outlet port E2 and the valve body 3, and between the outlet port E3 and the valve body 3, by sliding against the outer circumferential surface of the valve body 3.First to third coil springs SP1 to SP3, which are inserted with a predetermined preload into the respective spaces between the opening edges of the first line L1 and the inner side end surface of the sealing element S1, the opening edge of the line L3 and the inner side end surface of the second sealing element S2, and between the opening edge of the line L3 and the inner side end surface of the sealing element S3, so that they are positioned at the respective opening edges of the lines L1 to L3 in the respective outer end surfaces of the outlet ports E1 to E3, and which press the respective sealing elements S1 to S2 towards the valve body 3, and with known O-rings SL2, which are inserted into the respective spaces between the inner circumferential surface of the outlet port E1 and the outer circumferential surface of the sealing element S1, the inner circumferential surface of the outlet port E2 and the outer circumferential surface of the sealing element S2,and are positioned between the inner circumferential surface of the outlet connection E3 and the outer circumferential surface of the sealing element S3, so that they accommodate the concave sections that are cut out and formed on the respective inner circumferential surfaces of the outlet connections E1 to E3, and which seal the respective spaces between the outlet connection E1 and the sealing element S1, the outlet connections E2 and the sealing element S2, and between the outlet connection E3 and the sealing element S3, by sliding against the respective outer circumferential surfaces of the sealing elements S1 to S3.

[0022] The inner circumferential edges of one of the end faces of the respective sealing elements S1 to S3, one of which becomes the valve body side 3, are each provided with substantially conical, inclined first to third sealing surfaces S1a to S3a, which slide against the respective first to third sealing sliding parts D1 to D3. On the other side, flat first to third seating surfaces S1b to S3b, on which the respective end faces of the coil spring SP1 to SP3 are placed, are provided on the respective other end faces of the sealing elements S1 to S3. In this configuration, the sealing surfaces S1a to S3a slide against the sealing sliding parts D1 to D3 by so-called line contact, in which only the central parts (see in particular point F in Fig. 6(a)) in the lateral directions (in the radial directions) of the sealing surfaces S1a to S3a slide against the respective sealing sliding parts D1 to D3. Additionally, in the present embodiment, it is configured such that the sealing section F, at the time when the valve is closed, is within, with respect to the opening width of each of the first to third opening sections M1 to M3 mentioned below, in the direction of rotation of the valve body 3.

[0023] Additionally, as in Fig. 7 and Fig. As shown in Figure 8, a fourth outlet port E4 is formed through the other end of the valve body receiving part 13. The inner end of the fourth outlet port E4 faces the outer circumferential side passage 18, and a fourth line L4 is connected to the outer end of the fourth outlet port E4, and the cooling water is introduced into the throttle chamber TC. Thus, the bypass passage BL (see Figure 8) is closed. Fig. 1) configured. That is, the configuration has made it possible to always distribute the cooling water introduced into the outer circumferential side passage 18 to the throttle chamber TC via the fourth line L4, irrespective of the later-mentioned rotation phase of the valve body 3.

[0024] Furthermore, as in Fig. 3, Fig. 8 and Fig. As shown in Figure 9, a safety valve 20 is provided on the side of the third outlet port E3. In an emergency, when the valve body 3 cannot be actuated, for example due to a fault in an electrical system, the safety valve 20 is able to communicate with the valve body receiving part 13 (the outer circumferential side passage 18) of the third outlet port E3. The safety valve 20 is able to prevent overheating of the motor EG by ensuring the supply of cooling water to the radiator R3, even when the valve body 3 is in a stationary state.

[0025] The safety valve 20 is mainly configured with a substantially cylindrical flow-through forming element 21, which is received in a valve receiving port 11c that communicates the outer circumferential side passage 18 and the third line L3, and which initiates the inflow of cooling water from the inner end side (from the outer circumferential side passage 18 side); a thermocouple 22, which is provided to be received on the inner circumferential side of the flow-through forming element 21, and which is configured such that, when the temperature of the cooling water exceeds a predetermined temperature, wax (not shown in the drawings) filled into the thermocouple 22 expands, then a rod 22a of the thermocouple 22 moves to the outer end side of the flow-through forming element 21; and a valve element 23, which is located at the far end of the rod 22a of the thermocouple 21. Thermo-Elements 22 is fixed, and that is used,to open and close an outlet port 21a, opens at the outer end side of the flow passage forming element 21, and a helical spring 24, which is elastically installed with a predetermined preload between the valve element 23 and the flow passage forming element 21, and which pushes the valve element 23 in a valve-closing direction.

[0026] In the above configuration, under normal conditions (the temperature of the cooling water is lower than the specified temperature), an essentially conical inclined valve section 23a of the valve element 23 is pressed against the outer side connection edge of the outflow port 21a by the pressure force of the coil spring 24, thereby maintaining a valve closed state.On the other hand, in a high-temperature condition (the temperature of the cooling water is at the specified temperature or higher), the wax inside the thermo-element 22 expands, the valve element 23 moves to the outer end side of the flow-transmission-forming element 21 with the rod 22a against the pressing force of the helical spring 24, the valve element 23 is opened, and the inlet port, which is not shown in the drawings, and the outlet port 21a are in communication with each other, and thereby cooling water, introduced into the outer circumferential side passage 18, is supplied to the radiator RD through the third line L3.

[0027] In addition to an increase in the temperature of the cooling water, and also in a case where the pressure of the cooling water exceeds a predetermined pressure, the valve element 23 is pressed and retracted against the force of the helical spring 24, and the inlet port (not shown in the drawings) and the outlet port 21a are in communication with each other. This results in a reduction of the internal pressure of the flow control valve CV, thus preventing malfunctions in the flow control valve CV.

[0028] As in Fig. 3 and Fig. As shown in Figure 15, an end side of the second housing 12, which faces the first housing 11, is formed in a concave shape, extending over the valve body receiving part 13 and the motor receiving part 14 and is open so that it covers both of the receiving parts 13 and 14, and is fixed with a plurality of bolts BT1 on the other end side of the first housing 11 by a second flange section 12a, which is formed to extend from the outer circumferential area of ​​one end side opening, and a reduction gear mechanism receiving part 15, which receives the reduction gear mechanism 5, is formed between the second housing 12 and the other end side of the first housing 11.Additionally, at the time of joining the first and second housings 11 and 12, a circumferential sealing element SL3 is inserted between the connecting surfaces of the first and second housings 11 and 12, and thereby the interior of the reduction gear mechanism receiving part 15 is hermetically sealed.

[0029] The rotating shaft 2 is rotatably mounted on the bearing B1, which is received and positioned in a shaft insertion hole 11d formed by the end wall 11b, corresponding to the other end wall of the valve body receiving part 13. The valve body 3 is integrally rotatably fixed to one end section in the axial direction of the rotating shaft 2, and the second helical gear HG2 mentioned later is integrally rotatably fixed to the other end section in the axial direction of the rotating shaft 2. Additionally, a circumferential sealing element SL4 is placed between the outer circumferential surface of the rotating shaft 2 and the inner end side opening edge of the shaft insertion hole 11d, and the sealing element SL4 prevents the flow of cooling water from the valve body receiving part 13 to the reduction gear mechanism receiving part 15 through the space radially between the shaft insertion hole 11d and the rotating shaft 2.

[0030] The valve body 3 is integrally formed by casting with a predetermined synthetic resin material. As in Fig. 5 and Fig. 10 to Fig. As shown in Figure 12, one end of the valve body 3 is opened in the axial direction as an inlet port 3a, which is used for the inflow of cooling water introduced from the inlet port 10 of the first housing 11 to the inner circumferential side passage 17. On the other side, the other end of the valve body 3 is closed by an end wall 3b, and a plurality of substantially arcuate communication ports 3c, capable of communicating the inner circumferential side passage 17 with the outer circumferential side passage 18, are cut out and formed on the end wall 3b along a circumferential direction.Additionally, on the central part of the end wall 3d, corresponding to the axial center of the valve body 3, an essentially cylindrical shaft fixing section 3d, which is used to attach the rotary shaft 2, is formed to extend along the axial direction of the valve body 3, and an insertion element 3e, which is made of metal, is integrally formed on the inner circumferential side of the shaft fixing section 3d, and the rotary shaft 2 is pressed through the insertion element 3e.

[0031] Additionally, the valve body 3 is in a pillar shape (a shape in which capsules are connected to one another) in which the essential spherical sealing-sliding elements (the first to third sealing-sliding elements D1 to D3 mentioned later) are axially connected in series. These elements are used for the sealing action at the time of valve closure by sliding against the respective sealing elements S1 to S3. The opening / closing of each of the outlet ports E1 to E3 is effected by rotation within a predetermined angular range of approximately 180 degrees in the circumferential direction. In addition to rotation, the valve body 3 is rotatably mounted on a bearing B2, which is inserted into and held on an inner circumferential side of the inlet port 10 at one end by a bearing section 3g, the diameter of which is enlarged.

[0032] Regarding the formation of each of the sealing-sliding parts D1 to D3, the valve body 3 is essentially divided into two axial regions: a first axial region X1 at one end of the valve body 3, and a second axial region X2 at the other end. Additionally, these first and second axial regions X1 and X2 are essentially divided at a central position along the axial direction of the valve body 3, forming a boundary. Additionally, in each of the axial direction areas X1 or the axial direction areas X2, connecting edges of at least the first to third opening sections M1 to M3 mentioned later are formed in essentially spherical shapes in cross-section, that is, formed in curved surface shapes which have essentially the same curvature, and the curvature is set so that it is the same as the rotation radius of the valve body 3.

[0033] As in Fig. As shown in Figure 11(b), the first axial direction region X1 is formed from the first sealing-sliding part D1, which is provided over substantially half the circumference of the valve body 3 and which slides against the first sealing element S1, and the second sealing-sliding part D2, which is provided over the remaining half the circumference and which slides against the second sealing element S2. The first sealing-sliding part D1 is provided with the right-angled first opening section M1, which is positioned to have an axial direction region capable of substantially overlapping with the first outlet port E1 along the circumferential direction of the valve body 3.Similarly, the second sealing-sliding part D2 is provided with the oval-hole-shaped second opening section M2, which is set to have an axial direction width capable of substantially completely overlapping with the second outlet port E2 along the circumferential direction of the valve body 3.

[0034] In the present embodiment, as described above, the first opening section M1 is provided at a different circumferential position from the second opening section M2 in the first axial direction area X1, so that they overlap with each other in the rotation axis direction of the valve body 3, and thereby the size in the axial direction of the valve body 3 is reduced.

[0035] Additionally, regarding the overlap position mentioned above, it is not limited to the position in which they completely overlap in the axial direction, as in the present embodiment. For example, as in Fig. As shown in Figure 18, it is sufficient to arrange the valve 3 such that at least part of each of the opening sections M1 to M2 overlaps with the opening section M3 in the direction of rotation. This arrangement allows the valve 3 to be shortened in the axial direction by the amount of the overlap.

[0036] As in Fig. As shown in Figure 11(a), the second axial direction region X2 is formed from the third sealing-sliding part D3, which extends over half the circumference or more of the valve body 3 and slides against the third sealing element S3, and a non-sealing-sliding part D4, which extends over the remaining circumferential region and is not opposite the third outlet port E3, and is not used for the sealing action by the third sealing element S3. The third sealing-sliding part D3 is provided with the oval-hole-shaped third opening section M3, which is positioned to have an axial direction width capable of substantially overlapping the third outlet port E3 along the circumferential direction of the valve body 3.

[0037] Additionally, an auxiliary suction port M4, which has a right-angled shape in plan view, is provided on the non-sealing sliding part D4, along the circumferential direction of the valve body 3. The auxiliary suction port M4 is used to supply cooling water flowing in the outer circumferential side passage 18 to the inner circumferential side passage 17. In addition to the inlet port 3a, the auxiliary suction port M4 allows cooling water to be introduced into the inner circumferential side passage 17, and a larger quantity of cooling water is drawn into the interior of the inner circumferential side passage 17 and discharged from each of the outlet ports E1 to E3, thereby reducing the cooling water supply resistance.Additionally, since the non-sealing sliding part D4 is a so-called unused area, the non-sealing sliding part D4 is designed in a flat shape, like a non-spherical surface shape, which differs from the first to the third sealing sliding parts D1 to D3, which are designed in essentially spherical shapes, and consequently the weight of the valve body and the consumption of material forming the valve body 3 are reduced.

[0038] The shape and circumferential position of each of the first to the third opening sections M1 to M3, as provided above, are set such that their communication states with the first to third outlet ports E1 to E3 are changed by the rotation of the valve body 3 to form first to fourth states, which in Fig. 16 are shown and described later.

[0039] Additionally, as in Fig. As shown in Figure 11(b), the first axial direction region X1 is formed in a first valve opening region O1 and a second valve opening region O2, used for valve opening by the first and second opening sections M1 and M2, and a first valve closing region C1 and a second valve closing region C2, used for valve closing by the first and second sealing elements S1 to S2. This is comparable to the representation in Figure 11(b). Fig. As shown in Figure 11(a), the second axial direction region X2 is formed from a third valve opening region O2, which is used for valve opening, by the third opening section M3, a third valve closing region C3, used for valve closing by the third sealing element S3, and an unused region UA, which forms the non-sealing sliding section D4.

[0040] In the first axial direction region X1, a concave first level difference section N1, which is radially recessed inwards, is cut out and formed linearly continuously from one end face to the other end face of the valve body 3 at the circumferential direction end of the first opening section M1, which forms the area surrounding the boundary section between the first valve opening region O1 and the first valve closing region C1. Similarly, in the first and second axial direction regions X1 and X2, a concave second level difference section N2, which is radially recessed inwards, is cut out and formed linearly continuously from one end face to the other end face of the valve body 3 at the circumferential direction end of the third opening section M3, which forms the area surrounding the boundary section between the third valve opening region O3 and the third valve closing region C3.

[0041] Here, in the first to third sealing-sliding parts D1 to D3 and the non-sealing-sliding part D4, as in Fig. 11(a) shown, since the third sealing-sliding part D3 is positioned in a circumferential direction area which exceeds 180 degrees with respect to the casting of the valve body 3, a design form divided into three parts is used to avoid a so-called undercut. In particular, as shown in Fig. 11(a) and Fig. As shown in Figure 11(b), a first area A1 is formed by a first shape, a second area A2 is formed by a second shape, and a third area A3 is formed by a third shape.

[0042] As in Fig. As shown in Figure 12(a), in the central part in the width direction of the first level difference part N1, a first dividing line P1 is formed at the connecting part between the first form and the second form. As shown in Fig. As shown in Figure 12(b), in the central part in the width direction of the second level difference section N2, a second dividing line P2 is formed at the connecting part between the second form and the third form. Furthermore, as shown in Fig. As shown in Figure 12(c), a third dividing line is formed at the connecting part between the first form and the third form. In other words, the valve body 3 is formed by the first to the third form such that the first to the third dividing lines P1 to P3 are formed at the respective circumferential positions of the valve body 3.

[0043] Additionally, a pair of contact sections 3f, 3f is provided to limit the rotation of the valve body 3 at both end sections of the third valve closing area C3 in the other end part of the valve body 3, due to the level difference shape of the valve body 3. As shown in Fig. 10 and Fig. As shown in Figure 11, these contact sections 3f, 3f are provided so that they are able to bear against a rotation limiting section 11e, which projects from the other end-side-circumferential wall of the valve body receiving part 13. By bearing against the rotation limiting section 11e, the rotation range of the valve body 3 is limited within the specified angular range. These contact sections 3f, 3f are necessarily formed when the valve body 3 is formed. Thus, by using these contact sections 3f, 3f, there is no need to specifically provide a stop for limiting the rotation, and this leads to a cost reduction, etc., of the flow control valve CV.

[0044] As in Fig. 14 and Fig. As shown in Figure 15, the electric motor 4 is attached to and fixed to the opening edge portion of the motor mounting part 14 by a plurality of bolts BT2, by means of a flange section 4b provided on the base end portion of the motor body 4a, in a state in which the motor body 4a has been received into the motor mounting part 14 of the first housing 11, and the motor output shaft 4c extends to the inner side of the reduction gear mechanism mounting part 15 of the second housing 12 through one end side opening of the motor mounting part 14. Additionally, the electric motor is driven and controlled by an electronic control unit (not shown in the drawings) mounted on a vehicle, and controls the rotation of the valve body 3 according to a vehicle operating condition, thereby achieving a suitable distribution of the cooling water to the radiator RD, etc.

[0045] The reduction gear mechanism 5 is a drive mechanism formed from two worm gears and is configured as shown in Fig. 13 to Fig. Figure 15 shows a first worm gear G1 for decelerating the rotation of the electric motor 4 in cooperation with the motor output shaft 4c, and a second worm gear G2, which is connected to the first worm gear G1 and which further decelerates the rotation of the electric motor 4, which is transmitted by the first worm gear G1, and transmits this to the rotating shaft 2. The worm gear G2 is arranged essentially orthogonally to the first worm gear G1.

[0046] The first worm gear G1 is configured from a first helical gear WG1, which is integrally provided on the outer circumference of the motor output shaft 4c, and which rotates integrally with the motor output shaft 4c, and a first spindle gear HG1, which is integrally provided with its outer circumference on an end face of a rotating shaft 30, which is orthogonal to the first helical gear WG1, which is substantially parallel to the motor output shaft 4c, and which reduces the rotation of the first helical gear WG1 by engaging with the first helical gear WG1 and outputs it.

[0047] The second worm gear G2 is configured from a second worm gear WG2, which is integrally provided on the outer circumference at the other end side of the rotating shaft 30, and which rotates integrally with the first spindle gear HG1, and a second spindle gear HG2, which is fixed on the outer circumference at the other end side of the rotating shaft 2, which is arranged orthogonally to the first worm gear WG1, so that it is able to rotate integrally with the rotating shaft 2, and which reduces the rotation of the second worm gear WG2 by engaging with the second worm gear WG2 and outputs it.

[0048] The following describes a specific operating state of the CV flow control valve based on... Fig. 16 explained. To simplify the explanation, in order to distinguish the relative relationship between the outlet connections E1 to E3 and the respective opening sections M1 to M3, in Fig. 16, the first to third opening sections M1 to M3 of the valve body 3 are drawn by broken lines, the first to third outlet connections E1 to E2 of the first housing 11 are drawn by hatching and a state in which the E1 to E3 communicate with M1 to M3 is drawn in black.

[0049] This means that the electric motor 4 is controlled by control current, calculated on the basis of the vehicle operating conditions, and output by an electronic control unit not shown in the drawing, and the rotary position (phase) of the valve body 3 of the flow control valve CV is controlled, so that the relative relationship between the outlet ports E1 to E3 and the respective opening sections M1 to M3 is following each state according to the vehicle operating conditions.

[0050] In an initial state, which is in Fig. As shown in Figure 16(a), all first to third opening sections M1 to M3 are in a non-communication state with respect to the outlet ports E1 to E3. In this first state, the cooling water is not supplied to any of the heater heat exchanger HT, the oil cooler OC, or the radiator RD.

[0051] Next to the first state, in a second state, shown in Fig. 16(b), only the first opening section M1 is in a communication state, and the second and third opening sections M2 and M3 are in the non-communication state. Therefore, in the second state, due to the communication states, the cooling water is supplied to the heater-heat exchanger HT only from the first outlet port E1 through the first line L1. Furthermore, due to the overlap between the first outlet port E1 and the first opening section M1, the supply rate (the supply amount) of cooling water to the heater-heat exchanger HT is changed.

[0052] Next to the second state, in a third state, shown in Fig. 16(c), only the third opening section M3 is in the non-communication state. The first and second opening sections M1 and M2 are in the communication states. In the third state, due to these communication states, the cooling water to the heater heat exchanger HT and the oil cooler OC is supplied from the first and second outlet ports E1 and E2 through the first and second lines L1 and L2. Furthermore, due to the overlap between the first outlet port E1 and the first opening section M1, and between the second outlet port E2 and the second opening section M2, the supply rate (the supply amounts) of the cooling water to the heater heat exchanger HT and the oil cooler OC is changed.

[0053] Next to the third state, in a fourth state, shown in Fig. 16(d), all communication states from the first to the third opening sections M1 to M3 are related to the respective outlet ports E1 to E3. Therefore, in the fourth state, cooling water is supplied to all of the heater-heat exchanger HT, the oil cooler OC, and the radiator RD. Furthermore, due to the overlap between the first outlet port E1 and the first opening section M1, between the second outlet port E2 and the second opening section M2, and between the third outlet port E3 and the third opening section M3, the supply rates (supply amounts) of cooling water to the heater-heat exchanger HT, the oil cooler OC, and the radiator RD are changed.

[0054] The following describes a characteristic of an operating effect of the flow control valve CV according to the present embodiment, based on Fig. 17 explained.

[0055] As mentioned above, in the conventional flow control valve, since a convex parting line formed by casting protrudes from a sealing area of ​​the valve body, a sealing element slides against the parting line and therefore there is a risk that the sealing surface of the sealing element is damaged by the parting line.

[0056] In contrast, in the flow control valve CV according to the present embodiment, the concave first and second level difference parts N1 and N2, which are further excluded, are the outer circumferential surfaces of the first to third sealing-sliding parts D1 to D3, which are sealing-sliding contact surfaces, and the first and second division lines P1 and P2 are each provided in the level difference parts N1 and N2, and a disadvantage, namely that the sealing surface S1a slides against the division line P1 and each of the sealing surfaces S2a and S3a slides against the division line P2, is suppressed when the sealing surface S1a of the sealing element S1 passes through the division line P1 and each of the sealing surfaces S2a and S3a of the respective sealing elements S2 and S3 passes through the division line P2, and thus it is possible to damage the To suppress sealing surfaces S1 to S3 due to sliding against the division line P1 and P2.

[0057] Furthermore, since the first and second level difference parts N1 and N2 are radially inwardly concave, it has become possible to easily position the first and second division lines P1 and P2 in the first and second level difference parts N1 and N2 respectively, and this leads to excellent manufacturing of the valve body 3.

[0058] On the other hand, with respect to the third division line P3, in the first axial direction area X1, the third division line P3 is positioned at the boundary between the first sealing-sliding part D1 and the second sealing-sliding part D2. This eliminates the disadvantage that each of the sealing surfaces S1a and S2a passes through (crosses) the third division line P3, but this is suppressed by the forward / backward rotation of the valve body 3, and thus it is possible to suppress damage to the sealing surfaces S1a and S2a due to sliding against the third division line P3. On the other hand, in the second axial direction area X2, the third division line P3 is positioned in the unused area UA, and a disadvantage that the third sealing surface S3a slides against the third division line P3 is suppressed, and thus it is possible to suppress damage to the third sealing surface S3a due to sliding against the third division line P3.

[0059] Additionally, the first level difference part N1 is formed so that it is continuously connected to the sealing-sliding part D1, and the second level difference part N2 is formed so that it is continuously connected to the sealing-sliding parts D2 and D3 by soft curved surfaces, and it is possible that an edge section in the boundary part formed with each of the level difference parts N1 and N2 is suppressed, and thus it is possible to more effectively suppress damage to the sealing surfaces S1a to S3a when the sealing element S1 passes through the level difference part N1 and each of the sealing elements S2 and S3 passes through the level difference part N2.

[0060] Additionally, the circumference width of each of the first and second level difference parts N1 and N2 is smaller than that of each of the first to third sealing elements S1 to S3. Consequently, as in Fig. As shown in Figure 17, a disadvantage is that the sealing element S1 falls into the first level difference part N1, and the sealing elements S2 and S3 fall into the second level difference part N2, is suppressed and thus it is possible to obtain a soft sliding contact of each of the sealing elements S1 to S3.

[0061] Additionally, with regard to the first and second level difference parts N1 and N2, most parts of these are provided at the circumferential ends of the first to third opening sections M1 to M3, and this makes it possible to form each of the opening sections M1 to M3 integrally, without parts of each in the middle, and this leads to an excellent manufacture of the valve body 3 and cost reduction.

[0062] Furthermore, the first and second division lines P2 and P2 are continuously formed from one end side to the other end side of the axis of rotation direction of the valve body 3, and this leads to an excellent manufacturing of the valve body 3.

[0063] Additionally, in the present embodiment, since it is configured such that the sealing section F of each of the sealing surfaces S1a to S3a is positioned within the opening width of each of the first to the third opening sections M1 to M3 in the direction of rotation of the valve body 3 at the time of valve closure, even if the sealing surfaces S1a to S3a are damaged due to sliding against the opening edges of the opening sections M1 to M3, it is possible to maintain an excellent sealing action through each of the sealing surfaces S1a to S3a.

[0064] Furthermore, in the reception and storage of the sealing elements S1 to S3 in the respective first to third outlet ports E1 to E3, since the insert section 19 is provided on the inner side of each of the outlet ports E1 to E3, it becomes possible to further reduce the gap between the inner circumferential surface of the first housing 11 and the outer circumferential surface of the valve body 3 by the insert section 19, and thus it is possible to suppress the protrusion of each of the sealing elements S1 to S3 from the respective inner side ends of the outlet ports E1 to E3. This suppresses the deformation of each of the sealing elements S1 to S3, and a stable sealing action can be achieved by each of the sealing elements S1 to S3.Furthermore, it becomes possible to suppress the abrasion of each of the sealing elements S1 to S3 (each of the sealing surfaces S1a to S3a) due to deformation, and consequently the durability of the sealing elements S1 to S3 is also improved.

[0065] Additionally, in the design of the insert section 19, the insert section 19 is integrally formed with the first housing 11, eliminating the need to provide the insert section 19 separately. This results in excellent manufacturing of the flow control valve CV. Furthermore, at this stage, the insert section 19 can be easily formed by casting, further improving the manufacturing of the flow control valve. Moreover, in a case where the housing 11 is cast with a resin material, the insert section 19 can be just as easily formed by injection molding. [Second embodiment]

[0066] Fig. Figure 19 shows a second embodiment of the flow control valve according to the present invention in which the structure of each of the first and second level difference parts N1 and N2 in the first embodiment has been modified. Additionally, the configuration of the second embodiment is the same as that of the first embodiment except for the structure of each of the first and second level difference parts N1 and N2 and the structure accompanying the formation of each of the level difference parts N1 and N2 described below.

[0067] This means that in the present embodiment, the first and second level difference parts N1 and N2 are not formed in a concave shape (groove shapes) as shown in the first embodiment, but rather as stepped parts, by creating a difference in curvature at the front and rear, in the circumferential direction, of each of the level difference parts N1 and N2, and in the circumferential direction of each of the sliding sealing sections S1 to D3. The first and second division lines P1 and P2 are positioned in the respective stepped parts.

[0068] In the above configuration of the present invention, a disadvantage is that the sealing surface S1a to sealing element S1 slides against the division line P1, and each of the sealing surfaces S2a and S3a of the respective sealing elements S2 and S3 slides against the division line P2, as well as when the sealing surface S1a passes through the division line, and when each of the sealing surfaces S2a and S3a passes through the division line P2, and thus it is possible to suppress damage to the sealing surfaces S1a to S3a due to sliding against the division line P1 and P2.

[0069] Furthermore, in the case of the present embodiment, since the first and second level difference parts N1 and N2 are formed by changing the curvature of the outer circumferential surface of the valve body 3, that is, by changing the curvature at the front and rear of each of the level difference parts N1 and N2 in the circumferential direction, it is not necessary to form each of the level difference parts N1 and N2 separately, and this leads to excellent manufacturing of the valve body 3 and cost reduction.

[0070] Additionally, the first and second level difference parts N1 and N2 according to the exemplary embodiment are not formed in concave shapes, like the level difference parts of the first exemplary embodiment, but in simple stepped parts. This is consistent with the following, as shown in Fig.19(b), at least a portion of the first sealing surface S1a slides against the level difference section N1, and a portion of each of the second sealing surfaces S2a and S3a slides against the second level difference section N2 at the time the sealing elements S1 pass through to S3. However, in this case, a sliding contact section forms the outer end edge of each of the sliding surfaces S1a and S3a, and it is possible to prevent sliding against the sealing section F. Consequently, damage to the sealing section F due to sliding against each of the level difference sections N1 and N2 can be suppressed.

[0071] The present invention is not limited to the configuration according to each of the embodiments of the present invention. For example, regarding the size of each of the first to the third outlet ports E1 to E3, the number, arrangement (circumferential position) and shape of each of the first to the third opening sections M1 to M2, and the flow direction of the cooling water (from the inlet port 10 to each of the outlet ports E1 to E3), and likewise regarding the number of each of the level difference sections N1 to N2 (the number of divisions of the mold for forming the valve body 3), the circumferential direction position (arrangement) of each of the division lines P1 and P2, etc., as long as the above-mentioned working effect is obtained, this can be freely changed and modified according to the specification of the flow control valve CV.

[0072] In particular, in the present invention, it is sufficient that in the valve body 3 each of the division lines P1 and P2 is provided at a position in which each of the sealing elements S1 to S3 does not slide against the division lines P1 and P2, and only one embodiment is included in which the level difference parts N1 and N2 are provided, and the division lines P1 and P2 are each positioned in the level difference parts N1 and N2 as in the embodiment mentioned above, but also a mode (corresponding to the third division line 3) in which each of the division lines P1 and P2 is positioned in an unused area, obtained, for example, by increasing the diameter of the valve body 3.

[0073] Additionally, as in the embodiment described above, part of the division line P1 is provided in the sliding contact area of ​​the sealing element S1, and part of the division line P2 is provided in the sealing contact area of ​​each of the sealing elements S2 and S3. The level difference section N1 is formed in the sealing sliding section D1, and N2 is pre-formed in the sealing sliding sections D2 and D3. Division lines P1 and P2 are each provided within the level difference sections N1 and N2, respectively. Consequently, it becomes possible to reduce the non-sealing sliding section, which is an unused area, and it is therefore advantageous that the diameter of the valve body 3 can be reduced.

[0074] On the other hand, by providing a part of each of the division lines P1 and P2 in the non-sliding contact areas of the sealing elements S1 to S3 by positioning each of the division lines P1 and P2 on the non-sealing sliding contact part, which becomes the unused area, machining is not necessary when each of the division lines P1 and P2 is formed, and it is an advantage that this leads to an excellent manufacturing of the valve body 3.

[0075] Additionally, in each of the embodiments, although the present invention has been explained as an example in which the flow control valve CV is applied to a circulating system for cooling water, it is unnecessary to say that the flow control valve CV can be applied not only to cooling water, but to various fluids such as lubricating oil.

[0076] For example, the following aspects can be considered for the flow control valve based on the embodiment described above.

[0077] That is to say, in one aspect of the flow control valve, the flow control valve includes: a housing that has: a main communication port for introducing or discharging fluid, provided on a valve body receiving part which is formed in a hollow shape; and a plurality of communication ports, each of which communicates with the valve receiving part from a radial direction and supplies the fluid to or from the valve receiving part; a valve body which is rotatably mounted in the housing and has a plurality of opening sections whose overlapping states with the respective communication ports are changed according to a rotational position of the valve body;and sealing elements arranged between the housing and the valve body, the sealing elements sealing the space radially between the valve body and the housing by sliding against the outer circumferential surface of the valve body, wherein level difference parts lower than sliding contact surfaces of the valve body are provided radially inward in the sliding contact surfaces against which the sealing elements slide, with areas in which at least the communication ports and the respective opening sections overlap in the circumferential area of ​​the valve body.

[0078] In a preferred aspect of the flow control valve, the level difference parts are formed by concave parts that are radially recessed inwards.

[0079] In another preferred aspect, in any of the aspects of the flow control valve, the circumference of each of the concave parts is smaller than that of each of the sealing elements passing through the concave parts.

[0080] In another preferred aspect, in any of the aspects of the flow control valve, the sliding contact surfaces of the valve body and the concave parts are continuously connected by soft curved surfaces.

[0081] In another preferred aspect, in any of the aspects of the flow control valve, each of the concave parts is provided in the circumferential ends of the opening sections.

[0082] In another preferred aspect, in any of the aspects of the flow control valve, each concave part is provided continuously from one end side to the other end side in the direction of rotation of the valve body.

[0083] In another preferred aspect, in any of the aspects of the flow control valve, each of the level difference parts is formed by changing the curvature of the outer circumference of the valve body.

[0084] In another preferred aspect, in any of the aspects of the flow control valve, in a state in which the communication ports and the respective opening sections do not overlap, the sliding contact sections of each of the sealing elements within are oriented with respect to the opening width in each of the opening sections in the rotation axis direction of the valve body.

[0085] In another preferred aspect, in any of the aspects of the flow control valve, the majority of opening sections are provided at different circumferential positions of the outer circumference of the valve body, and at least part of one of the opening sections overlaps with one of the opening sections in the direction of rotation of the valve body.

[0086] In another preferred aspect, in any of the aspects of the flow control valve, insert sections are provided for sliding guidance of the sealing elements at the respective inner side ends of the communication ports.

[0087] In another preferred aspect, in any of the aspects of the flow control valve, each of the insert sections is integrally formed with the housing.

[0088] In another preferred aspect, in any of the aspects of the flow control valve, the valve body is formed by injection molding of a synthetic resin.

[0089] Additionally, from another point of view, a flow control valve, in one aspect of which, includes sealing elements arranged radially between a housing and a valve body which is rotatably mounted within the housing.The sealing elements seal the space radially between the housing and the valve body by sliding against the outer circumferential surface of the valve body, wherein the flow of fluid flowing from or into the inner circumferential side of the valve body is modified by changing the overlap states between communication ports that communicate the interior and exterior of the housing and respective opening sections that communicate the interior and exterior of the valve body, wherein level difference parts lower than sliding contact surfaces of the valve body are provided radially inward at the sliding contact surfaces against which the sealing elements slide, within areas in which at least the communication ports and the respective opening sections overlap, into the circumferential area of ​​the valve body.

[0090] Additionally, from another perspective, a flow control valve, in its first aspect, comprises: a housing having: a main communication port for introducing or discharging fluid, provided on a valve body receiving part formed in a hollow shape; and a plurality of communication ports, each communicating with the valve receiving part from a radial direction, and introducing or discharging the fluid into the valve receiving part; a valve body rotatably mounted in the housing, and having a plurality of opening sections, the overlapping states of which with the respective communication ports are changed according to the rotational position of the valve body;and sealing elements arranged between the housing and the valve body, the sealing elements sealing the space radially between the valve body and the housing by sliding against the outer circumferential surface of the valve body, with parting lines being provided at positions that do not slide against the sealing elements in the valve body.

[0091] In a preferred aspect of the flow control valve, at least a portion of each of the division lines is provided within a region in which the sealing elements slide against the outer circumferential surface of the valve body, in the circumferential region of the valve body.

[0092] In another preferred aspect, in any one of the aspects of the flow control valve, at least a part of each of the division lines is provided within a region in which the sealing elements do not slide against the outer circumferential surface of the valve body, in the circumferential region of the valve body.

[0093] In another preferred aspect, in any of the aspects of the flow control valve, surfaces on which the sealing elements that slide against the outer surface of the valve body are formed in spherical shapes in the outer circumference of the valve body, and a surface on which the sealing elements do not slide against the outer circumferential surface of the valve body is formed in a non-spherical shape in the circumference of the valve body.

Claims

[1] A flow control valve (CV) comprising: a housing (1) which has: a main communication port (10) for introducing or discharging fluid, provided on a valve body receiving part (13) which is designed in a hollow shape; and a plurality of communication ports (E1-E3), each of which communicates with the valve body receiving part (13) from a radial direction, and is configured to supply or discharge fluid into the valve body receiving part (13); a valve body (3) rotatably mounted in the housing (1) and has a plurality of opening sections (M1-M3) whose overlapping states with the respective communication ports (E1-E3) are changed according to the rotational position of the valve body (3); and Sealing elements (S1-S3) arranged between the housing (1) and an outer circumferential surface of the valve body (3) in a radial direction with reference to a rotational axis of the valve body (3), Division lines (P1, P2, P3) provided on the outer circumferential surface of the valve body (3), wherein at least one of the division lines (P1, P2, P3) is provided at positions on the outer circumferential surface of the valve body (3) that is not facing the sealing elements (S1-S3) at any point in any area of ​​the valve body (3) during actuation. [2] The flow control valve (CV) according to claim 1, wherein surfaces on which the sealing elements (S1-S3) which slide against the outer circumferential surface of the valve body (3) are formed in spherical shapes in the outer circumference of the valve body (3), and wherein a surface on which the sealing elements (S1-S3) do not slide against the outer circumferential surface of the valve body (3) in the circumference of the valve body (3) is formed in a non-spherical shape. [3] The flow control valve (CV) according to claim 2, which further comprises the level difference parts (N1, N2) which extend radially inwards beyond at least one of the surfaces on which the sealing elements (S1-S3) slide against the outer circumferential surface of the valve body (3), wherein the part of at least one of the division lines (P1, P2) is provided at a transition area between the level difference parts (N1, N2) and the at least one of the surfaces on which the sealing elements (S1-S3) slide against the outer circumferential surface of the valve body (3).

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