WO2025205353A1 - Valve device - Google Patents

Abstract

A valve device (1) is provided with a housing (10, 20), a drive valve (40), and a fixed valve (30). The drive valve (40) has a groove part (42) recessed from a sliding contact surface (41) in a manner that spans inner holes (36) and an outer hole (34) of the fixed valve (30) at a predetermined rotational position. The inner wall surface of the groove part (42) has a first inner wall surface (421) provided at a position corresponding to the inner holes (36), second inner wall surfaces (422) provided at positions corresponding to the outer hole (34), and connection surfaces (423) for connecting the first inner wall surface (421) and the second inner wall surfaces (422) in a curved manner or a planar manner. When assuming virtual lines (44) which result from an intersection between a first virtual surface obtained by extending the first inner wall surface (421) in the rotation direction and second virtual surfaces obtained by radially inwardly extending opposite surfaces (424) which are respectively opposite to the second inner wall surfaces (422), the distance (D1) between the connection surfaces (423) facing each other in the rotation direction is greater than the distance (D2) between the virtual lines (44) facing each other in the rotation direction.

Description

Valve equipment CROSS-REFERENCE TO RELATED APPLICATIONS

This application is based on Japanese Patent Application No. 2024-049895, filed on March 26, 2024, the contents of which are incorporated herein by reference.

This disclosure relates to a valve device that controls the flow of a fluid.

The valve device described in Patent Document 1 comprises a cylindrical fixed valve and a drive valve that is rotatable around a rotation axis relative to the fixed valve. The fixed valve has an inner passage formed in an annular shape around the rotation axis, and multiple outer passages formed in a fan shape radially outward from the inner passage. Meanwhile, the drive valve has a passage that connects the inner passage of the fixed valve with a specified outer passage at a specified rotation position. The passage of the drive valve has an arc-shaped inner wall surface that corresponds to the shape of the inner passage of the fixed valve, and a fan-shaped inner wall surface that corresponds to the shape of the outer passage.

DE 102021109743

However, in the valve device described in Patent Document 1, the cross-sectional area of the flow path in the drive valve passage is small at the point where the arc-shaped inner wall surface and the fan-shaped inner wall surface connect. Therefore, this valve device increases the pressure loss of the fluid flowing through the drive valve passage. As a result, when this valve device is applied to a fluid circulation system, the pumping capacity required for the fluid pump that circulates the fluid through the system must be increased, resulting in problems such as increased manufacturing costs and a larger size.

The purpose of this disclosure is to provide a valve device that can reduce fluid pressure loss.

According to one aspect of the present disclosure, a valve device for controlling fluid flow comprises:
Housing and
an actuated valve that is rotatable around a predetermined axis inside the housing;
a fixed valve fixed to the housing so as to be in sliding contact with a sliding contact surface of the drive valve that faces the direction in which the axis extends,
the housing has an inner passage provided around the axis in a region opposite the driven valve with respect to the fixed valve, an outer passage provided radially outward from the inner passage, and an inner/outer passage partition wall separating the inner passage from the outer passage;
the fixed valve has an inner hole provided at a position corresponding to the inner passage, an outer hole provided at a position corresponding to the outer passage, and an intermediate partition provided at a position corresponding to the inner/outer passage partition wall;
The actuated valve has a groove recessed from the sliding surface so as to span the inner hole and the outer hole at a predetermined rotational position,
the inner wall surface of the groove portion has a first inner wall surface provided at a position corresponding to the inner hole, a second inner wall surface provided at a position corresponding to the outer hole, and a connecting surface that connects the first inner wall surface and the second inner wall surface in a curved or flat shape at a position corresponding to the intermediate partition portion;
The first inner wall surface is formed in an arc shape centered on the axis,
the distance between opposing surfaces of the second inner wall surface that face each other in the rotational direction gradually increases from the connection surface toward the radially outer side,
When a virtual line is assumed where a first virtual plane obtained by extending the first inner wall surface in the rotational direction and a second virtual plane obtained by extending the opposing surface of the second inner wall surface inward in the radial direction intersect,
The distance between the connecting surfaces facing each other in the rotational direction is greater than the distance between the imaginary lines facing each other in the rotational direction.

This makes it possible to increase the cross-sectional area of the flow path between the connecting surfaces that face each other in the direction of rotation in the groove. Therefore, when fluid flows in the order of inner passage → inner hole → groove → outer hole → outer passage, or vice versa, it is possible to reduce the pressure loss of the fluid flowing between the connecting surfaces that face each other in the direction of rotation in the groove. Therefore, when this valve device is applied to a fluid circulation system, it is possible to reduce the pumping capacity required of the fluid pump that circulates the fluid through the system. As a result, it is possible to reduce the manufacturing costs of the valve device and fluid circulation system and make them more compact.

FIG. 1 is a perspective view of a valve device according to a first embodiment. FIG. 2 is a cross-sectional view of the valve device according to the first embodiment. 3 is a cross-sectional view showing a state where the rotational position of the actuated valve is changed in part III of FIG. 2. FIG. FIG. 4 is a perspective view of a portion corresponding to FIG. 3 . 4 is a plan view showing only the fixed valve taken along line VV in FIG. 3. FIG. 6 is a plan view showing only the actuated valve taken along line VI-VI in FIG. 3. 7 is a cross-sectional view taken along line VII-VII in FIG. 3, in which the shape of the sliding surface of the actuated valve is superimposed. 5 is a diagram showing the distance between connecting surfaces of actuating valves in the valve device according to the first embodiment; FIG. FIG. 10 is a diagram showing the distance between linear shapes of actuated valves in a valve device of a first comparative example. 10 is a graph comparing the water flow resistance between the valve device of the first embodiment and the valve device of the first comparative example. FIG. 10 is a diagram showing a state in which the actuated valve is in a nominal center position. FIG. 10 is a diagram showing the maximum positional deviation state of the drive valve in terms of design. FIG. 10 is a diagram showing a state in which the actuated valve is displaced further than the maximum positional displacement state in design. 14 is a graph comparing the overlap between the sliding contact surface of the actuated valve and the fixed valve in each of the states of FIGS. 11 to 13. FIG. 14 is a graph comparing the amount of fluid leakage into the adjacent outer passage in each of the states of FIGS. 11 to 13. FIG. 10 is a diagram showing a state in which the actuated valve in the valve device of the second comparative example is further displaced from the maximum positional displacement state in design. 17 is a graph comparing the overlap between the sliding contact surface of the actuating valve and the fixed valve in the states shown in FIGS. 13 and 16 . 17 is a graph comparing the amount of fluid leakage into the adjacent outer passage in each state shown in FIGS. 13 and 16. FIG. 6 is a partial cross-sectional view of a valve device according to a second embodiment. FIG. 20 is a schematic diagram of part XX in FIG. 19 . FIG. 20 is a schematic diagram of a portion corresponding to the XX portion in FIG. 19 in a valve device of a third comparative example. FIG. 8 is a cross-sectional view of a portion corresponding to FIG. 7 in a valve device according to a third embodiment.

Embodiments of the present disclosure will be described below with reference to the drawings. Note that, in the following embodiments, identical or equivalent parts will be designated by the same reference numerals, and their description will be omitted.

(First embodiment)
The valve device 1 of the first embodiment is used in a fluid circulation system mounted on, for example, an electric vehicle or a hybrid vehicle. The fluid circulation system circulates coolant fluid through a power source for driving the vehicle, a radiator, a heater core for air conditioning in the vehicle interior, and the like. For example, LLC (Long Life Coolant) containing ethylene glycol is used as the coolant. The valve device 1 switches the flow path of the coolant flowing through the system, adjusts the flow rate, and so on.

First, the configuration of the valve device 1 will be described.
As shown in FIGS. 1 to 4, the valve device 1 is a disc valve including housings 10, 20, a fixed valve 30, a drive valve 40, an actuator 50, and the like.

In the following description, the direction perpendicular to the axis CL of rotation of the drive valve 40 and radially outward from the axis CL in the direction of an imaginary circle centered on the axis CL is referred to as the "radially outward direction," and the direction toward the axis CL is referred to as the "radially inward direction." Furthermore, the direction in which the axis CL extends is referred to as the "axial direction," and the side of the housings 10, 20 on which the actuator 50 is provided is referred to as the "one axial side," and the opposite side is referred to as the "other axial side."

The housings 10, 20 are composed of a first housing 10 and a second housing 20, and have a fluid flow path inside. The first housing 10 has a cylindrical housing body 11, two fluid inlet ports 12, 13, and three fluid outlet ports 14, 15, 16 that extend from the housing body 11 in a pipe-like manner.

The two fluid inlet ports 12, 13 include a first fluid inlet port 12 and a second fluid inlet port 13. A first fluid inlet passage 102 is formed inside the first fluid inlet port 12, and a second fluid inlet passage 103 is formed inside the second fluid inlet port 13.

The three fluid outlets 14, 15, and 16 include a first fluid outlet 14, a second fluid outlet 15, and a third fluid outlet 16. A first fluid outlet passage 104 is formed inside the first fluid outlet 14, a second fluid outlet passage 105 is formed inside the second fluid outlet 15, and a third fluid outlet passage (not shown) is formed inside the third fluid outlet 16.

The second housing 20 closes the opening on one axial side of the housing main body 11. An actuator 50 is fixed to the second housing on the opposite side from the first housing.

The housing body 11 has a valve chamber 100, multiple inner passages 110, multiple outer passages 120, an inner passage partition wall 160, an inner/outer passage partition wall 130, and an outer passage partition wall 140 inside. The valve chamber 100 is provided with a fixed valve 30 and an actuated valve 40. The multiple inner passages 110 are arranged around the axis CL in an area of the fixed valve 30 opposite the actuated valve 40. The multiple outer passages 120 are arranged radially outward from the multiple inner passages 110. The multiple outer passages 120 have a first outer passage 121, a second outer passage 122, and a third outer passage (not shown). The multiple outer passages 120 are arranged to be aligned in the rotational direction of the actuated valve 40. The inner passage partition wall 160 is a wall that separates the multiple inner passages 110 from each other. The inner/outer passage partition wall 130 is a wall that separates the multiple inner passages 110 from the multiple outer passages 120. The outer passage partition wall 140 is a wall that separates the multiple outer passages 120 from each other.

The first fluid inlet passage 102 inside the first fluid inlet portion 12 extends from the multiple inner passages 110 of the housing body 11 to the other side in the axial direction. The second fluid inlet passage 103 inside the second fluid inlet portion 13 extends radially outward from the valve chamber 100 of the housing body 11.

The first fluid outlet passage 104 inside the first fluid outlet portion 14 extends radially outward from the first outer passage 121 of the housing body 11. The second fluid outlet passage 105 inside the second fluid outlet portion 15 extends radially outward from the second outer passage 122 of the housing body 11. The third fluid outlet passage (not shown) inside the third fluid outlet portion 16 extends radially outward from the third outer passage (not shown).

The fixed valve 30 is formed in a roughly disk shape and is placed on the valve chamber 100-side ends of the outer peripheral wall 150, outer passage partition wall 140, inner passage partition wall 160, inner/outer passage partition wall 130, and support portion 170, which are provided on the outer periphery of the outer passage 120 of the first housing 10. In other words, the fixed valve 30 is provided at the boundary between the inner passage 110 and outer passage 120 and the valve chamber 100. A seal member 60 is provided between the fixed valve 30 and the valve chamber 100-side ends of the outer peripheral wall 150, outer passage partition wall 140, inner/outer passage partition wall 130, inner passage partition wall 160, and support portion 170.

As shown in Figure 5, the fixed valve 30 has an outer peripheral portion 31, an intermediate partition portion 32, a central portion 33, an outer hole 34, an outer hole partition portion 35, an inner hole 36, and an inner hole partition portion 37. As shown in Figure 7, a protrusion 38 provided on the outer peripheral portion 31 is engaged with an engaging portion 17 provided on the first housing 10. This fixes the fixed valve 30 so that it cannot rotate relative to the housing main body 11 around the axis.

The inner hole 36 is located at a position corresponding to the inner passage 110 and is a hole that penetrates in the plate thickness direction. The outer hole 34 is located at a position corresponding to the outer passage 120 and is a hole that penetrates in the plate thickness direction. The outer holes 34 include a first outer hole 34a, a second outer hole 34b, a third outer hole 34c, and a fourth outer hole 34d. The first outer hole 34a communicates with the first outer passage 121. The second outer hole 34b and the fourth outer hole 34d communicate with the second outer passage 122. The third outer hole 34c communicates with the third outer passage.

The intermediate partition 32 is provided circumferentially between the inner hole 36 and the outer hole 34, separating the inner hole 36 and the outer hole 34 radially, and is placed on the inner/outer passage partition wall 130 of the first housing 10 with the seal member 60 sandwiched between them. The outer hole partition 35 is provided radially between the multiple outer holes 34, separating the multiple outer holes 34 circumferentially, and is placed on the outer passage partition wall 140 of the first housing 10 with the seal member 60 sandwiched between them.

As shown in Figures 4, 6, and 7, the actuated valve 40 is formed in a generally disk shape and is rotatably mounted in the valve chamber 100 of the housing body 11 around a predetermined axis CL. The surface of the actuated valve 40 facing the other side in the axial direction (i.e., the surface facing the fixed valve 30) is called the sliding surface 41. The sliding surface 41 of the actuated valve 40 and the fixed valve 30 are in sliding contact with each other.

The drive valve 40 has a groove 42 recessed from the sliding surface 41 toward one side in the axial direction, and a through-hole 43 that penetrates in the axial direction. The groove 42 is arranged to straddle the inner hole 36 and the outer hole 34 when the drive valve 40 is in a predetermined rotational position. The detailed shape of the groove 42 will be described later.

2, a shaft 70 is inserted through the centers of the drive valve 40 and the fixed valve 30. A holder 71 is fixed to one axial side of the shaft 70. The shaft 70 and holder 71 are integrally formed, for example, by insert molding. The holder 71 is rotatably supported by a bearing 72 provided in the second housing 20. The shaft 70 passes through an insertion hole 47 provided in the cylindrical portion 46 of the drive valve 40 and a central hole 39 in the fixed valve 30. The end of the shaft 70 on the other axial side is rotatably supported by the inner wall of a support portion 170 provided in the first housing 10. A gear 73 provided on one axial side of the holder 71 meshes with a gear of a torque transmission mechanism (not shown) of the actuator 50. A lever 74 is provided between the holder 71 and the drive valve 40. The lever 74 connects the holder 71 and the drive valve 40 in the rotational direction. Therefore, the torque output by the actuator 50 is transmitted from the holder 71 to the actuated valve 40 via the lever 74.

A compression spring 75 and a torsion spring 76 are provided between the holder 71 and the lever 74. One end of the compression spring 75 is engaged with the holder 71, and the other end is engaged with the lever 74, pressing the lever 74 and the drive valve 40 toward the fixed valve 30 relative to the holder 71. One end of the torsion spring 76 is engaged with the holder 71, and the other end is engaged with the lever 74, pressing the lever 74 and the drive valve 40 in the rotational direction relative to the holder 71.

The actuator 50 includes an electric motor (not shown), a torque transmission mechanism (not shown), and a control unit (not shown). When the actuator 50 is driven, the torque output by the electric motor is transmitted via the torque transmission mechanism from the holder 71 to the shaft 70 and lever 74 to the actuated valve 40. Therefore, with the sliding surface 41 of the actuated valve 40 in sliding contact with the fixed valve 30, the holder 71, shaft 70, springs 75, 76, lever 74, and actuated valve 40 rotate together around the axis CL relative to the housings 10, 20 and fixed valve 30.

As shown in FIG. 4, when the actuated valve 40 is in a predetermined rotational position, as indicated by arrow LF1, fluid flowing in from the first fluid inlet passage 102 flows in the following order: inner passage 110, inner hole 36, groove 42, first outer hole 34a, first outer passage 121, and first fluid outlet passage 104. Also, as indicated by arrow LF2 in FIG. 4, when the actuated valve 40 is in a predetermined rotational position, fluid flowing in from the second fluid inlet passage 103 flows in the following order: valve chamber 100, through-hole 43, second outer hole 34b, second outer passage 122, and second fluid outlet passage 105.

Next, we will explain the shape of the groove portion 42 of the drive valve 40.

As shown in Figure 6, the inner wall surface of the groove portion 42 has a first inner wall surface 421, a second inner wall surface 422, and a connecting surface 423. For ease of explanation, in Figure 6, the range of the first inner wall surface 421, the range of the second inner wall surface 422, and the range of the connecting surface 423 are each indicated by double-headed arrows. In addition, the range of the opposing surface 424 of the second inner wall surface 422 that faces the rotational direction is also indicated by a double-headed arrow.

7 shows the shape of the sliding surface 41 side of the actuated valve 40 in a dashed line in the cross-sectional view taken along line VII-VII in FIG. 3. As shown in FIG. 7, the first inner wall surface 421 is a surface provided at a position corresponding to the inner hole 36. The first inner wall surface 421 is formed in an arc shape centered on the axis CL. The second inner wall surface 422 is a surface provided at a position corresponding to the outer hole 34. The distance between opposing surfaces 424 of the second inner wall surface 422 that face in the rotational direction gradually increases from the connecting surface 423 toward the radially outward direction. When the actuated valve 40 is in a predetermined rotational position, the opposing surfaces 424 and the outer edge of the outer hole partition portion 35 of the fixed valve 30 that faces in the rotational direction are formed parallel to each other. The connecting surface 423 is a surface that connects the first inner wall surface 421 and the second inner wall surface 422 in a curved shape at a position corresponding to the intermediate partition portion 32. As will be described in the third embodiment below, the connection surface 423 may connect the first inner wall surface 421 and the second inner wall surface 422 in a planar manner.

As shown in Figure 7, the boundary position 425 between the opposing surface 424 of the second inner wall surface 422 and the connecting surface 423 at the sliding surface 41 side of the drive valve 40 is located closer to the axis CL than the surface 321 of the intermediate partition section 32 that faces radially outward. Note that the boundary position 425 between the opposing surface 424 of the second inner wall surface 422 and the connecting surface 423 is the point where the radius of curvature changes between the second inner wall surface 422 and the connecting surface 423.

The radius of curvature of the connection surface 423 is greater than half the radial width of the intermediate partition section 32. In other words, the connection surface 423 is not simply a chamfered finish at the connection point between the first inner wall surface 421 and the second inner wall surface 422, but rather increases the flow path cross-sectional area at the connection point between the first inner wall surface 421 and the second inner wall surface 422.

As shown in Figures 3 and 4, the inner wall surface of the groove portion 42 that faces the fixed valve 30 is called the "groove bottom surface 426." The surface of the first inner wall surface 421 that faces the axis center CL is called the "first inner wall vertical surface 427." The surface of the second inner wall surface 422 that faces the axis center CL is called the "second inner wall vertical surface 428." The connection point 429 between the groove bottom surface 426 and the first inner wall vertical surface 427 is a concave curved surface that is recessed on the side opposite the fixed valve 30. In addition, the connection point 430 between the groove bottom surface 426 and the second inner wall vertical surface 428 is also a concave curved surface that is recessed on the side opposite the fixed valve 30.

Next, the significance of providing the connection surface 423 in the groove portion 42 of the drive valve 40 will be explained with reference to Figures 8 to 10.

Figure 8 shows the shape of the groove 42 as seen from the sliding surface 41 side of the drive valve 40 in the valve device 1 according to the first embodiment. As shown in Figure 8, the distance between connecting surfaces 423 that face each other in the rotational direction is designated as D1. In the first embodiment, by providing the connecting surface 423 on the inner wall surface of the groove 42 of the drive valve 40, it is possible to increase the flow path cross-sectional area at the connection point between the first inner wall surface 421 and the second inner wall surface 422.

In contrast, Figure 9 shows the shape of the groove 42 as seen from the sliding surface 41 of the actuated valve 40 in the valve device of the first comparative example. As shown in Figure 9, in the first comparative example, the groove 42 of the actuated valve 40 does not have a connecting surface 423. Therefore, in the first comparative example, the connecting point between the opposing surface 424 of the second inner wall surface 422 and the first inner wall surface 421 is a linear shape 44. The distance between the linear shapes 44 facing each other in the rotational direction is D2.

In the first comparative example, the linear shape 44 at the connection point between the second inner wall surface 422 and the first inner wall surface 421 corresponds to the imaginary line at the intersection of the first imaginary plane extending the first inner wall surface 421 in the rotational direction and the second imaginary plane extending the opposing surface 424 radially inward in the first embodiment.

The distance D1 between the connection surfaces 423 that face each other in the rotational direction in the groove portion 42 of the first embodiment shown in Figure 8 is greater than the distance D2 between the linear shapes 44 that face each other in the rotational direction in the groove portion 42 of the first comparative example shown in Figure 9. Therefore, the flow path cross-sectional area between the connection surfaces 423 that face each other in the rotational direction in the groove portion 42 of the first embodiment is greater than the flow path cross-sectional area between the linear shapes 44 that face each other in the rotational direction in the groove portion 42 of the first comparative example.

Figure 10 is a graph comparing the water flow resistance of the groove portion 42 of the first embodiment with the water flow resistance of the first comparative example. The water flow resistance of the groove portion 42 of the first embodiment is smaller than the water flow resistance of the first comparative example. Note that water flow resistance can also be interpreted as pressure loss.

Increasing the connection surface 423 reduces fluid pressure loss (i.e., water flow resistance), but the tradeoff is a new problem: an increase in the amount of fluid leaking from a given outer passage 120 through which the fluid flows to an adjacent outer passage 120. Therefore, as shown in Figure 11, in the valve device 1 of the first embodiment, the boundary position 425 between the opposing surface 424 of the second inner wall surface 422 and the connection surface 423 is located closer to the axial center CL than the surface 321 of the intermediate partition section 32 facing radially outward.

The significance of the boundary position 425 between the opposing surface 424 of the second inner wall surface 422 and the connecting surface 423 in the valve device 1 of the first embodiment as described above will be explained with reference to Figures 11 to 18.

Figures 11 to 13 show the variation in the rotational position of the actuated valve 40 when the actuator 50 controls the rotational position of the actuated valve 40 and causes fluid to flow from the inner passage 110 to the inner hole 36 to the groove 42 to the first outer hole 34a to the first outer passage 121. Specifically, Figure 11 shows the actuated valve 40 in its nominal center position. Figure 12 shows the actuated valve 40 in its maximum design position deviation state. Figure 13 shows the actuated valve 40 in its position deviation even greater than the maximum design position deviation state (hereinafter referred to as the "outer state of design variation").

Figure 14 is a graph comparing the overlap between the sliding surface 41 of the actuated valve 40 and the fixed valve 30 in the area surrounded by dashed line A in Figures 11 to 13. The overlap is largest when the actuated valve 40 is in the nominal center position, small when the actuated valve 40 is in the maximum designed positional deviation state, and even smaller when the actuated valve 40 is in the outermost state of the designed variation. The overlap functions as a sealing surface between the sliding surface 41 of the actuated valve 40 and the fixed valve 30.

Figure 15 is a graph comparing the amount of leakage of fluid from the groove 42 to the adjacent outer passage (e.g., fourth outer hole 34d → second outer passage 122) when the valve device 1 flows fluid in the order of inner passage 110 → inner hole 36 → groove 42 → first outer hole 34a → first outer passage 121. As shown in Figure 15, the amount of leakage to the adjacent outer passage is smallest when the actuated valve 40 is in the nominal center position, slightly larger when the actuated valve 40 is in the maximum design position deviation state, and even larger when the actuated valve 40 is in the outer state with design variation.

Here, a valve device of a second comparative example will be described for comparison with the valve device 1 of the first embodiment. As shown in FIG. 16, the valve device of the second comparative example has a larger connection surface 423 of the groove portion 42 compared to the first embodiment. Specifically, in the second comparative example, the boundary position 425 between the opposing surface 424 of the second inner wall surface 422 and the connection surface 423 is located radially outward from the surface 321 of the intermediate partition portion 32 that faces radially outward. FIG. 16 shows the rotational position of the drive valve 40 in an outer state due to design variation. In this state, a gap S is formed between the connection surface 423 of the groove portion 42 and the intermediate partition portion 32 and outer hole partition portion 35 of the fixed valve 30. Fluid leaks from the groove portion 42 to the adjacent outer passage through this gap S.

Figure 17 is a graph comparing the overlap between the sliding surface 41 of the actuating valve 40 and the fixed valve 30 in the area surrounded by dashed line A in Figures 13 and 16 when the design variation is outside the limits. As shown in Figure 17, when the design variation is outside the limits, the overlap is on the positive side in the first embodiment, but on the negative side in the second comparative example. In other words, the graph shows that in the second comparative example, there is no overlap, and a gap S is formed between the connection surface 423 of the groove 42 and the intermediate partition portion 32 and outer hole partition portion 35 of the fixed valve 30.

Figure 18 is a graph comparing the amount of leakage of fluid from the groove 42 to the adjacent outer passage (e.g., fourth outer hole 34d → second outer passage 122) when the valve device 1 flows fluid in the order of inner passage 110 → inner hole 36 → groove 42 → first outer hole 34a → first outer passage 121. As shown in Figure 18, in the outer state of design variation, the amount of leakage to the adjacent outer passage is significantly greater in the second comparative example than in the first embodiment. Therefore, it can be seen that when the boundary position 425 between the opposing surface 424 and the connecting surface 423 of the second inner wall surface 422 is located radially outward of the surface 321 of the intermediate partition section 32 facing radially outward, as in the second comparative example, the amount of leakage to the adjacent outer passage is significantly greater.

Compared to the first and second comparative examples, the valve device 1 of the first embodiment has the following advantages:

(1) In the first embodiment, the inner wall surface of the groove portion 42 of the actuated valve 40 has a first inner wall surface 421 corresponding to the inner bore 36, a second inner wall surface 422 corresponding to the outer bore 34, and a connecting surface 423 that connects the first inner wall surface 421 and the second inner wall surface 422 in a curved shape. Here, the linear shape 44 of the connecting portion between the second inner wall surface 422 and the first inner wall surface 421 described in the first comparative example corresponds to a virtual line in the first embodiment where a first virtual plane extending from the first inner wall surface 421 in the rotational direction intersects with a second virtual plane extending from the opposing surface 424 radially inward. Therefore, as shown in FIGS. 8 and 9 , in the first embodiment, the distance D1 between the connecting surfaces 423 facing each other in the rotational direction is greater than the distance D2 between the virtual lines facing each other in the rotational direction.
This allows the cross-sectional area of the flow path between the connection surfaces 423 that face each other in the rotational direction in the groove 42 to be increased. Therefore, when the fluid flows in the order of the inner passage 110 → inner hole 36 → groove 42 → outer hole 34 → outer passage 120, or in the reverse order, it is possible to reduce the pressure loss of the fluid flowing between the connection surfaces 423 that face each other in the rotational direction in the groove 42. Therefore, when this valve device 1 is applied to a fluid circulation system, it is possible to reduce the pumping capacity required for the fluid pump that circulates the fluid through the system. As a result, the manufacturing costs of the valve device and the fluid circulation system can be reduced and the size can be made smaller.

(2) However, increasing the area of the connecting surface 423 reduces the pressure loss of the fluid, but at the same time, a new problem arises in that the amount of fluid leaking from a given outer passage 120 through which the fluid flows increases to an adjacent outer passage 120. Therefore, in the first embodiment, on the inner wall surface of the groove portion 42 of the drive valve 40, the boundary position 425 between the opposing surface 424 of the second inner wall surface 422 and the connecting surface 423 is located closer to the axis CL than the surface 321 of the intermediate partition portion 32 that faces radially outward.
As a result, even if the groove portion 42 of the actuated valve 40 is misaligned from a predetermined outer passage 120 through which the fluid flows toward an adjacent outer passage 120, an overlapping margin can be secured between the outer hole partition portion 35 and the intermediate partition portion 32 of the fixed valve 30 and the sliding contact surface 41 of the actuated valve 40. This makes it possible to prevent fluid from leaking from the predetermined outer passage 120 through which the fluid flows to the adjacent outer passage 120. Therefore, the valve device 1 can simultaneously reduce the pressure loss of the fluid flowing through the groove portion 42 and reduce the leakage of fluid from the predetermined outer passage 120 through which the fluid flows toward the adjacent outer passage 120.

(3) In the first embodiment, a connection point 429 between a groove bottom surface 426 of the inner wall surface of the groove portion 42 facing the fixed valve 30 and a first inner wall vertical surface 427 of the first inner wall surface 421 facing the axis center CL is a concave curved surface. In addition, a connection point 430 between the groove bottom surface 426 and a second inner wall vertical surface 428 of the second inner wall surface 422 facing the axis center CL is also a concave curved surface.
This suppresses the generation of vortices at the connection point 429 between the groove bottom surface 426 and the first inner wall vertical surface 427, and at the connection point 430 between the groove bottom surface 426 and the second inner wall vertical surface 428, thereby reducing the pressure loss of the fluid flowing through the groove portion 42.

Second Embodiment
The second embodiment is different from the first embodiment in that the shape of the groove 42 of the actuated valve 40 is partially changed, but the rest of the second embodiment is the same as the first embodiment, so only the differences from the first embodiment will be described.

As shown in Figures 19 and 20, in the second embodiment, the first inner wall vertical surface 427 of the groove portion 42 of the actuated valve 40 is inclined toward the axis CL from the sliding surface 41 toward the groove bottom surface 426. In addition, the second inner wall vertical surface 428 of the groove portion 42 of the actuated valve 40 is also inclined toward the axis CL from the sliding surface 41 toward the groove bottom surface 426. For the sake of explanation, the inclination angles of the first inner wall vertical surface 427 and the second inner wall vertical surface 428 are depicted as being larger than they actually are in Figure 20. The inclination angles of the first inner wall vertical surface 427 and the second inner wall vertical surface 428 with respect to the axis CL need only be greater than 0 degrees.

Furthermore, in the groove portion 42 of the drive valve 40, the connection point 429 between the groove bottom surface 426 and the first inner wall vertical surface 427 is a concave curved surface recessed on the side opposite the fixed valve 30. Furthermore, in the groove portion 42 of the drive valve 40, the connection point 430 between the groove bottom surface 426 and the second inner wall vertical surface 428 is also a concave curved surface recessed on the side opposite the fixed valve 30.

Here, a valve device of a third comparative example will be described for comparison with the valve device 1 of the second embodiment. As shown in FIG. 21 , in the third comparative example, the first inner wall vertical surface 427 and the second inner wall vertical surface 428 of the groove portion 42 of the actuated valve 40 are both parallel to the axis CL. When the actuated valve 40 is in a predetermined rotational position, fluid flows in the following order: inner passage 110, inner hole 36, groove portion 42, outer hole 34, first outer passage 121, and first fluid outlet passage 104, as indicated by arrow LF1 in FIG. 21 . At this time, in the third comparative example, as indicated by arrows V1 and V2 in FIG. 21 , vortices generated at the connection point 429 between the groove bottom surface 426 and the first inner wall vertical surface 427 and the connection point 430 between the groove bottom surface 426 and the second inner wall vertical surface 428 become large, raising concerns about increased water flow resistance.

In contrast, as shown in FIG. 20, in the second embodiment, both the first inner-wall vertical surface 427 and the second inner-wall vertical surface 428 are inclined toward the axis CL from the sliding surface 41 toward the groove bottom surface 426. Furthermore, the connection point 429 between the groove bottom surface 426 and the first inner-wall vertical surface 427 and the connection point 430 between the groove bottom surface 426 and the second inner-wall vertical surface 428 are both concavely curved. Therefore, as shown by arrows V3 and V4 in FIG. 20, vortices generated at the connection point 429 between the groove bottom surface 426 and the first inner-wall vertical surface 427 and the connection point 430 between the groove bottom surface 426 and the second inner-wall vertical surface 428 are reduced, thereby reducing water flow resistance. Therefore, the valve device 1 of the second embodiment can reduce pressure loss caused by a sudden change in direction when the fluid flows in a U-turn manner in the groove portion 42.

(Third embodiment)
The third embodiment will be described. In the third embodiment, the shape of the groove 42 of the actuated valve 40 is partially changed from that of the first embodiment, but the rest of the third embodiment is the same as that of the first embodiment, and therefore only the differences from the first embodiment will be described.

22 , in the third embodiment, the connecting surface 423 of the groove 42 of the actuated valve 40 is a surface that connects the first inner wall surface 421 and the second inner wall surface 422 in a planar manner. Note that, at the portion of the actuated valve 40 on the sliding surface 41 side, a boundary position 425 between the connecting surface 423 and an opposing surface 424 of the second inner wall surface 422 is located closer to the axis CL than the surface 321 of the intermediate partition portion 32 that faces radially outward.
The valve device 1 of the third embodiment described above can also achieve the same effects as those of the first embodiment and the like.

(Other embodiments)
In the above embodiments, the valve device 1 has been described as having two fluid inlets 12, 13 and three fluid outlets 14, 15, 16, but the number of fluid inlets and outlets can be changed as desired. Furthermore, the number of outer passages 120 and inner passages 110 provided in the housing 10 can also be changed as desired. Furthermore, the valve device 1 can also be used such that fluid flows in through the fluid outlets 14, 15, 16 and flows out through the fluid inlets 12, 13.

(2) In the above embodiments, the drive valve 40 has been described as having both a through hole 43 and a groove portion 42, but this is not limiting and the drive valve 40 may have only a groove portion 42.

The present disclosure is not limited to the above-described embodiments and may be modified as appropriate. Furthermore, the above-described embodiments and portions thereof are not unrelated to one another and may be combined as appropriate, except where such combinations are clearly impossible. Furthermore, in the above-described embodiments, it goes without saying that the elements constituting the embodiments are not necessarily essential, except where expressly stated as essential or where they are clearly considered essential in principle. Furthermore, in the above-described embodiments, when the number, numerical value, amount, range, etc. of the components of the embodiments are mentioned, they are not limited to that specific number, except where expressly stated as essential or where they are clearly limited to a specific number in principle. Furthermore, in the above-described embodiments, when the shape, positional relationship, etc. of the components, etc. are mentioned, they are not limited to that shape, positional relationship, etc., except where expressly stated as essential or where they are clearly limited to a specific shape, positional relationship, etc. in principle.

Claims (4)

In a valve device for controlling the flow of a fluid,
a housing (10, 20);
a drive valve (40) rotatable around a predetermined axis (CL) inside the housing;
a fixed valve (30) fixed to the housing so as to be in sliding contact with a sliding contact surface (41) of the drive valve that faces the direction in which the axis extends,
The housing has an inner passage (110) provided around the axis in a region opposite the drive valve with respect to the fixed valve, an outer passage (120) provided radially outward from the inner passage, and an inner/outer passage partition wall (130) separating the inner passage from the outer passage,
The fixed valve has an inner hole (36) provided at a position corresponding to the inner passage, an outer hole (34) provided at a position corresponding to the outer passage, and an intermediate partition (32) provided at a position corresponding to the inner/outer passage partition wall,
The actuated valve has a groove portion (42) recessed from the sliding contact surface so as to span the inner hole and the outer hole at a predetermined rotational position,
The inner wall surface of the groove portion has a first inner wall surface (421) provided at a position corresponding to the inner hole, a second inner wall surface (422) provided at a position corresponding to the outer hole, and a connecting surface (423) that connects the first inner wall surface and the second inner wall surface in a curved or flat shape at a position corresponding to the intermediate partition portion,
The first inner wall surface is formed in an arc shape centered on the axis,
The distance between opposing surfaces (424) of the second inner wall surface that face each other in the rotational direction gradually increases from the connection surface toward the radially outer side,
When a virtual line (44) is assumed where a first virtual plane extending from the first inner wall surface in the rotational direction intersects with a second virtual plane extending from the opposing surface of the second inner wall surface inward in the radial direction,
A valve device, wherein a distance (D1) between the connection surfaces facing each other in the rotational direction is greater than a distance (D2) between the imaginary lines facing each other in the rotational direction. The valve device described in claim 1, wherein the boundary position (425) between the opposing surface of the second inner wall surface and the connecting surface is located closer to the axis than the surface (321) of the intermediate partition portion facing radially outward. a connection point (429) between a groove bottom surface (426) of the inner wall surface of the groove portion facing the fixed valve side and a first inner wall vertical surface (427) of the first inner wall surface facing the axial center side is a concave curved surface;
3. The valve device according to claim 1, wherein a connection portion (430) between the groove bottom surface and a second inner wall vertical surface (428) of the second inner wall surface facing the axial center side is also concavely curved. the second inner wall vertical surface is inclined from the sliding contact surface side toward the groove bottom surface side toward the axis center side,
4. The valve device according to claim 3, wherein the first inner wall vertical surface also inclines from the sliding contact surface side to the groove bottom surface side toward the axis center side.