Switching device

Abstract

To provide a valve device capable of enhancing the function of a valve.SOLUTION: A valve device has a valve body comprising a plurality of valve ports, and a valve body assembly comprising valve elements that can be fitted into the valve ports, and the valve elements are simultaneously displaced relative to each valve port by moving the valve body assembly. Consequently, although the overall length of the valve body assembly can be reduced, the resolution of flow rate control can be increased, so that flow rate characteristics can be precisely controlled.SELECTED DRAWING: Figure 1

Description

Technical Field

[0001] The present invention relates to a valve device.

Background Art

[0002] For the flow rate control of fluids, various valve devices are used. As an example, the electric valve disclosed in Patent Document 1 is for the purpose of controlling the flow rate of a refrigerant in a refrigeration cycle system or the like, and can control the opening degree of an orifice by driving a valve body using a motor as power.

Prior Art Documents

Patent Documents

[0003]

Patent Document 1

Summary of the Invention

Problems to be Solved by the Invention

[0004] A valve device such as the electric valve shown in Patent Document 1 uses a single valve body, so there is a problem that the resolution of flow rate control is low and the function of the valve body is limited. On the other hand, if a long valve body is secured in the longitudinal direction and the valve body shape is finely adjusted, a certain degree of resolution can be ensured, but another problem occurs that the overall length of the valve body becomes long and the valve device cannot be made compact.

[0005] The present invention is made by focusing on a different perspective from the conventional one, and an object thereof is to provide a valve device capable of enhancing the function of a valve.

Means for Solving the Problems

[0006] To achieve the above object, the valve device of the present invention includes a first valve port that communicates the valve chamber with the first flow path, and a second valve port that communicates the valve chamber with the second flow path a valve body having the first valve port first that can be fitted into valve body and a second valve body that can be fitted into the second valve portA valve body assembly comprising, having, The first valve body includes a tapered portion in which the area of a cross section orthogonal to the moving direction of the first valve body changes as it goes in the moving direction of the first valve body. The second valve body includes a cylindrical portion in which the area of a cross section orthogonal to the moving direction of the second valve body is uniform. By moving the valve body assembly, for each valve port each The valve body is displaced simultaneously, When at least the cylindrical portion is located within the second valve port, the tapered portion is located within the first valve port. Characterized by the above.

Advantages of the Invention

[0007] According to the present invention, a valve device capable of enhancing the function of the valve can be provided.

Brief Description of the Drawings

[0008]

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Embodiments for Carrying Out the Invention

[0009] Hereinafter, as an embodiment of the present invention, an electrically driven valve which is a type of valve device will be described with reference to it. In this specification, the taper portion is a variable cross-sectional area portion whose cross-sectional area in a direction orthogonal to the moving direction of the valve body assembly changes, and the straight portion is a fixed cross-sectional area portion whose cross-sectional area in a direction orthogonal to the moving direction does not change.

[0010] <First Embodiment> FIG. 1 is a longitudinal sectional view showing a schematic configuration of an electric drive valve 10 according to a first embodiment. FIG. 2 is a view showing an enlarged periphery of a valve body assembly of the electric drive valve 10 shown in FIG. 1. FIG. 3 is a plan view of the valve body assembly. Let the axis of the electric drive valve 10 be L. Also, in this specification, the coil side is assumed to be upward and the valve body side is assumed to be downward.

[0011] In FIG. 1, the electric drive valve 10 includes a valve body 14 having a valve chamber 12, a valve body assembly 13, a cam 15 connected to the upper part of the valve body 14, a stator coil 18 disposed outside the cam 15, a rotor 16 that rotates by energization and excitation of the stator coil 18, a male screw member 17 attached to the valve body assembly 13, and a housing 19 that covers the outside of the stator coil 18.

[0012] The rotor 16 is rotatable about the axis L with respect to the cam 15 via a support member (not shown) and is fixed in the direction of the axis L. At the upper end of the rotor 16, the shaft portion 13b of the valve body assembly 13 is held via a bearing 20, and the shaft portion 13b is fitted to the rotor 16 so as to be relatively rotatable about the axis L and relatively movable in the direction of the axis L.

[0013] A female screw 16a is formed on the inner periphery of the rotor 16 and is screwed onto a male screw 17a formed on the outer periphery of the male screw member 17. The male screw member 17 is fixed to the outer periphery of the shaft portion 13b of the valve body assembly 13 and is movable in the direction of the axis L together with the valve body assembly 13. As the female screw 16a and the male screw 17a screw together in response to the rotation of the rotor 16, the male screw member 17 moves in the direction of the axis L with respect to the rotor 16.

[0014] The valve body 14 is formed separately from a bottomed cylindrical lower body portion 14a, a bottomed cylindrical middle body portion 14b, and a bottomed cylindrical upper body portion 14c, and is joined and integrated at the broken line position in FIG. 1. A lower opening 14d penetrates through the bottom wall of the lower body portion 14a, and a second pipe T2 is connected to the lower opening 14d.

[0015] A horizontal opening 14f is formed through the side wall of the middle body portion 14b, and a first pipe T1 is connected to the horizontal opening 14f. A first valve port 14g, a second valve port 14h, and a third valve port 14i penetrate through the bottom wall of the middle body portion 14b and are formed such that their centers are aligned on the same straight line. The first valve port 14g, the second valve port 14h, and the third valve port 14i each have a circular shape, and the cross-sectional area of the lower opening 14d is larger than the total cross-sectional area of them, and the cross-sectional area of the horizontal opening 14f is also larger.

[0016] A rectangular guide hole 14j is formed through the bottom wall of the upper body portion 14c. The horizontal opening 14f, the first valve port 14g, the second valve port 14h, and the third valve port 14i communicate with the valve chamber 12 so that the fluid can move.

[0017] In FIGS. 2 and 3, the valve body assembly 13 is formed by connecting a circular flange portion 13a and a shaft portion 13b connected to the center of the upper surface of the flange portion 13a. As the material of the valve body assembly 13, resins such as aluminum, brass, SUS, and PTFE can be used. The shaft portion 13b has a cross-sectional shape (non-circular shape) perpendicular to the axis equal to the rectangular cross-sectional shape of the guide hole 14j, and rotation around the axis L is prevented with respect to the guide hole 14j of the upper body portion 14c, but it is fitted so as to be movable in the direction of the axis L. The cross-sectional shapes of the shaft portion 13b and the guide hole 14j are not limited to rectangular as long as they are non-circular shapes.

[0018] On the lower surface of the flange portion 13a, a first valve body 13c is formed to be insertable into the first valve port 14g, a second valve body 13d is formed to be insertable into the second valve port 14h, and a third valve body 13e is formed to be insertable into the third valve port 14i. The overall length of the first valve body 13c is the shortest, and the overall length of the third valve body 13e is the longest.

[0019] As shown in Fig. 2, the first valve body 13c has a tapered shape with a reduced diameter toward the lower side. Specifically, from the flange portion 13a side, a first 11th tapered portion 13f and a first 12th tapered portion 13g with a larger taper angle than the first 11th tapered portion 13f are connected in series. The maximum outer diameter of the first 11th tapered portion 13f is equal to the inner diameter of the first valve port 14g. The axis L1 of the first valve body 13c is parallel to the axis L. Here, the taper angle refers to the inclination angle θ with respect to the axis of the valve body.

[0020] Also, the second valve body 13d includes, from the flange portion 13a side, a cylindrical 20th straight portion 13h, a 21st tapered portion 13i with a reduced diameter toward the lower side, and a 22nd tapered portion 13j with a larger taper angle than the 21st tapered portion 13i, which are connected in series. The outer diameter of the 20th straight portion 13h and the maximum outer diameter of the 21st tapered portion 13i are equal to the inner diameter of the second valve port 14h. The axis of the second valve body 13d overlaps with the axis L.

[0021] Also, the third valve body 13e includes, from the flange portion 13a side, a cylindrical 30th straight portion 13m, a 31st tapered portion 13n with a reduced diameter toward the lower side, and a 32nd tapered portion 13o with a larger taper angle than the 31st tapered portion 13n, which are connected in series. The outer diameter of the 30th straight portion 13m and the maximum outer diameter of the 31st tapered portion 13n are equal to the inner diameter of the third valve port 14i. The axis L3 of the third valve body 13e is parallel to the axis L.

[0022] In the present embodiment, in the direction of the axis L, the boundary between the first 11th tapered portion 13f and the first 12th tapered portion 13g coincides with the boundary between the 20th straight portion 13h and the 21st tapered portion 13i, and the boundary between the 21st tapered portion 13i and the 22nd tapered portion 13j coincides with the boundary between the 30th straight portion 13m and the 31st tapered portion 13n.

[0023] (Operation of the Electrically Driven Valve) In the state where the valve body assembly 13 is located at the upper stroke end (fully open valve position), the first valve body 13c is separated from the first valve port 14g, the second valve body 13d is separated from the second valve port 14h, and the third valve body 13e is separated from the third valve port 14i. In such a state, the fluid that has entered the valve chamber 12 from the first pipe T1 is discharged toward the second pipe T2 through all of the first valve port 14g, the second valve port 14h, and the third valve port 14i, so that a large-capacity fluid delivery can be performed.

[0024] When the rotor 16 rotates in one direction by energizing and exciting the stator coil 18 from the state where the valve body assembly 13 is located at the upper stroke end, relative rotation occurs between the male screw member 17, and the female screw 16a and the male screw 17a are screwed. Since the position of the rotor 16 is fixed in the axial direction, the male screw member 17 moves downward in the axial direction together with the valve body assembly 13. As a result, the first valve body 13c, the second valve body 13d, and the third valve port 14i are simultaneously displaced.

[0025] According to the rotation angle of the rotor 16, first, the third valve body 13e enters the third valve port 14i, then the second valve body 13d enters the second valve port 14h, and finally the first valve body 13c enters the first valve port 14g. By sequentially entering the valve ports in this way, fine flow rate control becomes possible.

[0026] In the state where the valve body assembly 13 is located at the lower stroke end (fully closed valve position), the first valve body 13c shields the first valve port 14g, the second valve body 13d shields the second valve port 14h, and the third valve port 14i is shielded by the third valve body 13e, so that the fluid in the valve chamber 12 is prevented from being discharged toward the second pipe T2.

[0027] According to the present embodiment, since the shaft portion 13b having a rectangular cross-sectional shape is fitted into the guide hole 14j, rotation around the axis L is prevented, whereby the first valve body 13c can surely enter the first valve port 14g, the second valve body 13d can surely enter the second valve port 14h, and the third valve body 13e can surely enter the third valve port 14i.

[0028] When the rotor 16 rotates in the reverse direction due to the energization and excitation of the stator coil 18 from the state where the valve body assembly 13 is located at the lower stroke end, first, the first valve body 13c separates from the first valve port 14g, then the second valve body 13d separates from the second valve port 14h, and finally the third valve body 13e separates from the third valve port 14i according to the rotation angle of the rotor 16, and finally reaches the upper stroke end.

[0029] (Example of adjustment of flow rate control) Hereinafter, an example of adjustment of the flow rate control of the electric drive valve 10 will be specifically described. FIG. 4 is a diagram showing the flow rate control characteristics of the electric drive valve 10, where the vertical axis represents the flow rate and the horizontal axis represents the relative position with respect to the valve port in the axial direction L of the valve body assembly (or valve body) (however, the fully closed valve position is set to 0). FIG. 5 is an enlarged cross-sectional view of the periphery of the valve port of the valve body according to the comparative example. FIGS. 6 to 11 are diagrams showing the change in the axial position of the valve body assembly 13.

[0030] The comparative example shown in FIG. 5 has a single circular valve port 14' having a cross-sectional area equal to the total cross-sectional area of the first valve port 14g, the second valve port 14h, and the third valve port 14i of the present embodiment, and a valve body 13' having a shape similar to that of the first valve body 13c.

[0031] (Comparative example) The broken line shown in FIG. 4 indicates the flow rate control characteristics according to the comparative example. In the comparative example, as the valve body 13' rises in the axial direction with respect to the circular valve port 14', the fluid flows out from the gap between the valve body 13' and the circular valve port 14', and the outflow rate of the fluid with respect to the valve body displacement amount is a linear relationship until the valve body 13' reaches the position p5.

[0032] When the valve body 13' of the comparative example rises above the position p5 shown in Fig. 4, the amount of fluid flowing out from the gap between the valve body 13' and the circular valve port 14' increases. When the position p7 shown in Fig. 4 is reached, the flow direction cross-sectional area of the gap between the valve body 13' and the upper end (valve seat) of the circular valve port 14' becomes equal to the cross-sectional area of the circular valve port 14'. Therefore, above the position p7 shown in Fig. 4, regardless of the position of the valve body 13', the outflow rate of the fluid becomes constant.

[0033] (Step 1: 0 to p1) On the other hand, the solid line shown in Fig. 4 indicates the flow rate control characteristics according to this embodiment. As the valve body assembly 13 rises from the fully closed valve position, first a gap is generated between the first valve body 13c and the first valve port 14g, and the outflow of fluid from the first valve port 14g is started. At this time, since the 20th straight portion 13h of the second valve body 13d is located within the second valve port 14h, and the 30th straight portion 13m of the third valve body 13e is also located within the third valve port 14i, the outflow of fluid from the second valve port 14h and the third valve port 14i is blocked. The outflow rate of the fluid with respect to the displacement amount of the valve body assembly 13 has a linear relationship up to the position p1. Since the cross-sectional area of the first valve port 14g is relatively small, the outflow rate can be suppressed to be smaller than that of the comparative example even at the same position.

[0034] (Step 2: p1 to p2) When the valve body assembly 13 reaches the position p1, as shown in FIG. 6, the boundary between the 11th tapered portion 13f and the 12th tapered portion 13g coincides with the upper end position of the first valve port 14g in the axial direction. At this time, since the 20th straight portion 13h of the second valve body 13d is located within the second valve port 14h and the 30th straight portion 13m of the third valve body 13e also remains located within the third valve port 14i, the outflow of fluid from the second valve port 14h and the third valve port 14i is blocked. Since the taper angle of the 12th tapered portion 13g is larger than the taper angle of the 11th tapered portion 13f, as the first valve body 13c separates from the first valve port 14g and rises in the axial direction, the amount of fluid outflow with respect to the displacement amount of the valve body assembly 13 becomes larger than that until the position p1, but is in a linear relationship until the valve body assembly 13 reaches the position p2, and the outflow amount can be suppressed to be smaller than that of the comparative example even at the same position.

[0035] (Step 3: p2 to p3) When the valve body assembly 13 reaches the position p2, as shown in FIG. 7, the tip of the 12th tapered portion 13g coincides with the upper end position of the first valve port 14g in the axial direction, and the boundary between the 20th straight portion 13h and the 21st tapered portion 13i of the second valve body 13d coincides with the upper end position of the second valve port 14h in the axial direction. Thereafter, in addition to the fluid flowing through the first valve port 14g, a gap is formed between the second valve body 13d and the second valve port 14h, and the outflow of fluid from the second valve port 14h is started. At this time, since the first valve body 13c is largely separated from the first valve port 14g, the amount of fluid flowing out from the first valve port 14g becomes constant, and since the 30th straight portion 13m of the third valve body 13e is located within the third valve port 14i, the outflow of fluid from the third valve port 14i is blocked. Therefore, the amount of fluid outflow with respect to the displacement amount of the valve body assembly 13 becomes smaller than that between the positions p1 and p2, and is in a linear relationship until the valve body assembly 13 reaches the position p3, and the outflow amount can be suppressed to be smaller than that of the comparative example even at the same position.

[0036] (Step 4: p3 to p4) When the valve body assembly 13 reaches the position p3, as shown in FIG. 8, the boundary between the 21st tapered portion 13i and the 22nd tapered portion 13j coincides with the upper end position of the second valve port 14h in the axial direction. At this time, the amount of fluid flowing out from the first valve port 14g remains constant, and since the 30th straight portion 13m of the third valve body 13e remains located within the third valve port 14i, the outflow of fluid from the third valve port 14i is blocked. Since the taper angle of the 22nd tapered portion 13j is larger than the taper angle of the 21st tapered portion 13i, as the second valve body 13d rises in the axial direction, the outflow rate of fluid with respect to the displacement amount of the valve body assembly 13 becomes larger than that between the positions p2 and p3, but it is a linear relationship until the valve body assembly 13 reaches the position p4, and the outflow rate can be suppressed to be smaller than that of the comparative example even at the same position.

[0037] (Step 5: p4 to p6) When the valve body assembly 13 reaches the position p4, as shown in FIG. 9, the tip of the 22nd tapered portion 13j coincides with the upper end position of the second valve port 14h in the axial direction, and the boundary between the 30th straight portion 13m and the 31st tapered portion 13n of the third valve body 13e coincides with the upper end position of the third valve port 14i in the axial direction. At this time, in addition to the amount of fluid flowing out from the first valve port 14g remaining constant, hereafter, the amount of fluid flowing out from the second valve port 14h also becomes constant. In addition, a gap is generated between the third valve body 13e and the third valve port 14i, and the outflow of fluid from the third valve port 14i is started. For this reason, the outflow rate of fluid with respect to the displacement amount of the valve body assembly 13 becomes smaller than that between the positions p3 and p4, and it is a linear relationship until the valve body assembly 13 reaches the position p6, and the outflow rate can be suppressed to be smaller than that of the comparative example even at the same position.

[0038] (Step 6: p6 to p7) When the valve body assembly 13 reaches position p6, as shown in FIG. 10, the boundary between the 31st tapered portion 13n and the 32nd tapered portion 13o coincides with the upper end position of the 3rd valve port 14i in the axial direction. At this time, the amount of fluid flowing out from the 1st valve port 14g and the amount of fluid flowing out from the 2nd valve port 14h are constant. Since the taper angle of the 32nd tapered portion 13o is larger than the taper angle of the 31st tapered portion 13n, as the 3rd valve body 13e ascends in the axial direction, the outflow rate of the fluid with respect to the displacement amount of the valve body assembly 13 becomes larger than that between position p4 and position p6, but it is a linear relationship until the valve body assembly 13 reaches position p7, and the outflow rate can be suppressed to be smaller than that of the comparative example even at the same position.

[0039] (Step 7: After p7) When the valve body assembly 13 reaches position p7, as shown in FIG. 11, the tip of the 32nd tapered portion 13o coincides with the upper end position of the 3rd valve port 14i in the axial direction. At this time, the amount of fluid flowing out from the 1st valve port 14g and the amount of fluid flowing out from the 2nd valve port 14h are constant, and thereafter the amount of fluid flowing out from the 3rd valve port 14i also becomes constant.

[0040] As is clear from comparing the dashed line and the solid line in FIG. 4, in the present embodiment, although the overall length of the valve body assembly 13 can be suppressed, the resolution of the flow rate control can be increased, and thereby the flow rate characteristics can be precisely controlled.

[0041] (Modification 1 of the 1st Embodiment) FIG. 12 is a plan view similar to FIG. 3 of the valve body assembly 13A according to Modification Example 1 of the first embodiment. In the above-described first embodiment, the valve bodies are arranged such that the centers of the valve bodies are in a line. However, in this modification, the centers of the first valve body 13Ac, the second valve body 13Ad, and the third valve body 13Ae are arranged at equal intervals along a circle coaxial with the center of the flange portion 13Aa. Although not shown, corresponding to the centers of the first valve body 13Ac, the second valve body 13Ad, and the third valve body 13Ae, the first valve port, the second valve port, and the third valve port are also arranged at equal intervals along a circle coaxial with the center of the valve body assembly 13A. Since the other configurations are the same as those of the first embodiment, redundant explanations are omitted.

[0042] (Modification Example 2 of the First Embodiment) FIG. 13 is a plan view similar to FIG. 3 of the valve body assembly 13B according to Modification Example 2 of the first embodiment. In the above-described first embodiment, the shaft portion had a rectangular cross-sectional shape. However, in this modification, the shaft portion 13Bb has a cylindrical shape and has a V-shaped groove (recess) 13Bs extending along the axis L direction. Although not shown, the guide hole into which the shaft portion 13Bb fits is also circular as a whole and has a protrusion (convex portion) protruding from the inner periphery. When the shaft portion 13Bb is fitted into the guide hole, the protrusion engages with the V-shaped groove. By engaging the guide hole and the shaft portion 13Bb, it is slidable in the axial direction but non-rotatable relative to each other. Therefore, the first valve body 13Bc can surely enter the first valve port, the second valve body 13Bd can surely enter the second valve port, and the third valve body 13Be can surely enter the third valve port. Note that a convex portion may be formed on the shaft portion, and a concave portion may be formed in the guide hole correspondingly. Since the other configurations are the same as those of the first embodiment, redundant explanations are omitted.

[0043] (Modification Example 3 of the First Embodiment) FIG. 14 is a plan view similar to FIG. 3 of the valve body assembly 13C according to Modification 3 of the first embodiment. Similar to Modification 1, the centers of the first valve body 13Cc, the second valve body 13Cd, and the third valve body 13Ce are arranged at equal intervals along a circle coaxial with the center of the flange portion 13Ca. Also, similar to Modification 2, the shaft portion 13Cb has a cylindrical shape and has a V-shaped groove (recess) 13Cs extending along the axial direction of the axis L. Since the other configurations are the same as those of the first embodiment, redundant descriptions are omitted.

[0044] (Modification 4 of the First Embodiment) FIG. 15 is a plan view similar to FIG. 3 of the valve body assembly 13D according to Modification 4 of the first embodiment. In Modification 3 described above, the flange portion 13Ca is circular, but in this modification, the shape of the flange portion 13Da as viewed in the axial direction is a hexagon (non-circular shape) in which the long sides and the short sides are alternately connected. One of the short sides abuts against the planar inner peripheral surface 14Ds of the middle body portion 14Db (shown by hatching) of the valve body 14D and is slidable relative to each other. By engaging the middle body portion 14Db and the flange portion 13Da, it is slidable in the axial direction but non-rotatable relative to each other, so that relative rotation around the axis between the valve body assembly 13D and the middle body portion 14Db is prevented. For this reason, the first valve body 13Dc can be reliably inserted into the first valve port, the second valve body 13Dd can be reliably inserted into the second valve port, and the third valve body 13De can be reliably inserted into the third valve port. In this modification, the shaft portion 13Db has a perfect cylindrical shape. Since the other configurations are the same as those of the first embodiment, redundant descriptions are omitted.

[0045] (Modification 5 of the First Embodiment) FIG. 16 is a plan view similar to FIG. 3 of the valve body assembly 13E according to Modification 5 of the first embodiment. In Modification 4 described above, the flange portion 13Da is hexagonal, but in this modification, the shape of the flange portion 13Ea when viewed in the axial direction is a rectangle having a long side and a short side, and the inner peripheral cross-section in the direction perpendicular to the axis of the middle main body portion 14Eb (shown by hatching) is also a rectangle corresponding to the flange portion 13Ea. The gap between the middle main body portion 14Eb and the flange portion 13Ea is exaggerated. By engaging the inner periphery of the middle main body portion 14Eb with the outer periphery of the flange portion 13Ea, it is slidable in the axial direction but cannot move relative to each other in the circumferential direction, so the relative rotation around the axis between the valve body assembly 13E and the middle main body portion 14Eb is blocked. Therefore, the first valve body 13Ec can be reliably inserted into the first valve port, the second valve body 13Ed can be reliably inserted into the second valve port, and the third valve body 13Ee can be reliably inserted into the third valve port. In this modification, the shaft portion 13Eb has a perfect cylindrical shape. Since the other configurations are the same as those of the first embodiment, duplicate descriptions are omitted.

[0046] (Modification 6 of the First Embodiment) FIG. 17 is a plan view similar to FIG. 3 of the valve body assembly 13F according to Modification 6 of the first embodiment. The shape of the flange portion 13Fa is similar to that of Modification 4 described above, but the inner peripheral surface in the direction perpendicular to the axis of the middle main body portion 14Fb (shown by hatching) has two concave grooves 14Fs that engage with the outer peripheral corners of the flange portion 13Fa and are relatively slidable in the axial direction. The gap between the concave groove 14Fs and the flange portion 13Fa is exaggerated. By engaging the concave groove 14Fs with the corners of the flange portion 13Fa, it is slidable in the axial direction but cannot rotate relative to each other, so the relative rotation around the axis between the valve body assembly 13F and the middle main body portion 14Fb is blocked. Therefore, the first valve body 13Fc can be reliably inserted into the first valve port, the second valve body 13Fd can be reliably inserted into the second valve port, and the third valve body 13Fe can be reliably inserted into the third valve port. In this modification, the shaft portion 13Fb has a perfect cylindrical shape. Since the other configurations are the same as those of the first embodiment, duplicate descriptions are omitted.

[0047] (Modification Example 7 of the First Embodiment) FIG. 18 is a plan view similar to FIG. 3 of the valve body assembly 13G according to Modification Example 7 of the first embodiment. With respect to Modification Example 1 described above, the arrangements of the first valve body 13Gc, the second valve body 13Gd, and the third valve body 13Ge are common, and the fact that the flange portion 13Ga is circular is common, but the difference is that a V-shaped notch (recess) 13Gs is formed on the outer periphery of the flange portion 13Ga. On the other hand, the inner peripheral surface in the direction perpendicular to the axis of the middle main body portion 14Gb (shown by hatching) has a protrusion (convex portion) 14Gs that engages with the notch 13Gs. By engaging the notch 13Gs and the protrusion 14Gs, it is slidable in the axial direction but cannot move relative to each other in the circumferential direction, so the relative rotation around the axis between the valve body assembly 13G and the middle main body portion 14Gb is prevented. For this reason, the first valve body 13Gc can be surely inserted into the first valve port, the second valve body 13Gd can be surely inserted into the second valve port, and the third valve body 13Ge can be surely inserted into the third valve port. In this modification, the shaft portion 13Gb has a perfect cylindrical shape. Note that a convex portion may be formed on the flange portion, and a corresponding concave portion may be formed on the middle main body portion. Since the other configurations are the same as those of the first embodiment, duplicate explanations are omitted.

[0048] (Second Embodiment) FIG. 19 is a diagram showing the flow rate control characteristics of the electric drive valve according to the second embodiment, where the vertical axis represents the flow rate and the horizontal axis represents the relative position of the valve body assembly with respect to the valve port in the axial direction (however, the fully closed valve position is set to 0). FIGS. 20 to 23 are diagrams showing the axial position of the valve body assembly according to the second embodiment changed. Since this embodiment is the same as the first embodiment except for the valve body assembly 13H, duplicate explanations are omitted.

[0049] In the first embodiment, as shown in FIG. 4, the outflow rate of the fluid with respect to the displacement amount of the valve body assembly tends to change greatly at the inflection point. However, according to this embodiment, the rate of change of the flow rate can be suppressed, and smoother flow rate control can be performed.

[0050] As shown in Fig. 20, the valve body assembly 13H is formed by connecting a circular flange portion 13Ha and a shaft portion 13Hb connected to the center of the upper surface of the flange portion 13Ha. Since the flange portion 13Ha and the shaft portion 13Hb are the same as those in the first embodiment, redundant description is omitted.

[0051] On the lower surface of the flange portion 13Ha, a first valve body 13Hc is formed to face the first valve port 14g, a second valve body 13Hd is formed to face the second valve port 14h, and a third valve body 13He is formed to face the third valve port 14i. The overall lengths of the first valve body 13Hc, the second valve body 13Hd, and the third valve body 13He are substantially equal.

[0052] As shown in Fig. 20, the first valve body 13Hc is formed by connecting, from the flange portion 13Ha side, a first tapered portion 13Hf that tapers downward as it goes downward, a cylindrical first straight portion 13Hg, and a twelfth tapered portion 13Hq having a larger taper angle than the tenth tapered portion 13Hf. The maximum outer diameter of the tenth tapered portion 13Hf is equal to the inner diameter of the first valve port 14g. The axis L1 of the first valve body 13Hc is parallel to the axis L.

[0053] Also, the second valve body 13Hd is formed by connecting, from the flange portion 13Ha side, a cylindrical twentieth straight portion 13Hh, a twenty-first tapered portion 13Hi that tapers downward as it goes downward, a cylindrical twenty-second straight portion 13Hj, and a twenty-third tapered portion 13Hk having a larger taper angle than the twenty-first tapered portion 13Hi. The outer diameter of the twentieth straight portion 13Hh and the maximum outer diameter of the twenty-first tapered portion 13Hi are equal to the inner diameter of the second valve port 14h. The axis of the second valve body 13Hd overlaps the axis L.

[0054] Also, the third valve body 13He is formed by connecting, from the flange portion 13Ha side, a cylindrical thirtieth straight portion 13Hm, a thirty-first tapered portion 13Hn that tapers downward as it goes downward, and a thirty-second tapered portion 13Ho having a larger taper angle than the thirty-first tapered portion 13Hn. The outer diameter of the thirtieth straight portion 13Hm and the maximum outer diameter of the thirty-first tapered portion 13Hn are equal to the inner diameter of the third valve port 14i. The axis L3 of the third valve body 13He is parallel to the axis L.

[0055] In this embodiment, in the direction of the axis L, the boundary between the 10th tapered portion 13Hf and the 11th straight portion 13Hg coincides with the boundary between the 20th straight portion 13Hh and the 21st tapered portion 13Hi. Also, the boundary between the 21st tapered portion 13Hi and the 22nd straight portion 13Hj coincides with the boundary between the 30th straight portion 13Hm and the 31st tapered portion 13Hn.

[0056] From the fully closed valve position, as shown in FIG. 20, when the valve body assembly 13H is raised until the boundary between the 10th tapered portion 13Hf and the 11th straight portion 13Hg coincides with the upper end of the first valve port 14g in the axial direction and the boundary between the 20th straight portion 13Hh and the 21st tapered portion 13Hi coincides with the upper end of the second valve port 14h in the axial direction, a flow rate change from 0 to position p11 as shown in FIG. 19 occurs. At this time, the third valve port 14i is shielded by the 30th straight portion 13Hm.

[0057] From position P11, as shown in FIG. 21, when the valve body assembly 13H is raised until the boundary between the 21st tapered portion 13Hi and the 22nd straight portion 13Hj coincides with the upper end of the second valve port 14h in the axial direction and the boundary between the 30th straight portion 13Hm and the 31st tapered portion 13Hn coincides with the upper end of the third valve port 14i in the axial direction, a flow rate change from position p11 to position p12 as shown in FIG. 19 occurs. At this time, the 11th straight portion 13Hg is disposed at the first valve port 14g, the amount of fluid passing through the first valve port 14g is constant, and the third valve port 14i is shielded by the 30th straight portion 13Hm.

[0058] From position P12, as shown in FIG. 22, when the valve body assembly 13H is raised until the boundary between the 11th straight portion 13Hg and the 12th tapered portion 13Hq coincides with the upper end of the first valve port 14g in the axial direction, the boundary between the 22nd straight portion 13Hj and the 23rd tapered portion 13Hk coincides with the upper end of the second valve port 14h in the axial direction, and the boundary between the 31st tapered portion 13Hn and the 32nd tapered portion 13Ho coincides with the upper end of the third valve port 14i in the axial direction, a flow rate change occurs from the position p12 shown in FIG. 19 to the position p13.

[0059] From position P13, as shown in FIG. 23, when the valve body assembly 13H is raised so as to be separated from the valve port, a flow rate change occurs from the position p13 shown in FIG. 19 to the position p14. Even if the valve body assembly 13H is raised above the position p14, the amount of fluid flowing out of the electrically driven valve remains constant.

[0060] According to the present embodiment, until the flow rate control at the first valve port 14g starts and ends, no flow rate change of the fluid flowing through the second valve port 14h and the third valve port 14i is caused (0 to p11). Also, until the flow rate control at the second valve port 14h starts and ends, no flow rate change of the fluid flowing through the first valve port 14g and the third valve port 14i is caused (p11 to p12). Further, until the flow rate control at the third valve port 14i starts and ends, no flow rate change of the fluid flowing through the first valve port 14g and the second valve port 14h is caused (p12 to p13). In this way, by causing the flow rate change at each valve port to be performed in a relay format, smooth flow rate control can be performed without causing a sudden flow rate change.

[0061] (Third Embodiment) FIG. 24 is a diagram showing the flow rate control characteristics of the electric drive valve according to the third embodiment, where the vertical axis represents the flow rate and the horizontal axis represents the relative position with respect to the valve port in the axial direction of the valve body assembly (with the fully closed valve position being 0). FIGS. 25 and 26 are diagrams showing the axial position of the valve body assembly according to the third embodiment being changed. In this embodiment, the valve body assembly 13I and the middle main body portion 14Ib are different from those in the first embodiment.

[0062] The middle main body portion 14Ib of this embodiment has a first valve port 14Ig and a second valve port 14Ih. Since the valve main body other than the middle main body portion 14Ib is the same as that in the first embodiment, duplicate explanations are omitted.

[0063] As shown in FIG. 25, the valve body assembly 13I is formed by connecting a circular flange portion 13Ia and a shaft portion 13Ib connected to the center of the upper surface of the flange portion 13Ia. Since the flange portion 13Ia and the shaft portion 13Ib are the same as those in the first embodiment, duplicate explanations are omitted.

[0064] On the lower surface of the flange portion 13Ia, a first valve body 13Ic is formed to face the first valve port 14Ig, and a second valve body 13Id is formed to face the second valve port 14Ih.

[0065] The first valve body 13Ic has a tapered shape that tapers downward in diameter. Specifically, from the flange portion 13Ia side, an eleventh tapered portion 13If and a twelfth tapered portion 13Ig with a larger taper angle than the eleventh tapered portion 13If are connected in series. The axis L1 of the first valve body 13Ic is parallel to the axis L.

[0066] Also, the second valve body 13Id has only a cylindrical twentieth straight portion 13Ih. A chamfer may be provided on the outer periphery of the tip of the twentieth straight portion 13Ih. The outer diameter of the twentieth straight portion 13Ih is equal to the inner diameter of the second valve port 14Ih. The axis L2 of the second valve body 13Id is parallel to the axis L.

[0067] From the fully closed position, as shown in Fig. 25, when the valve body assembly 13I is raised until the boundary between the 11th tapered portion 13If and the 12th tapered portion 13Ig coincides with the upper end of the first valve port 14Ig in the axial direction, a flow rate change occurs from 0 to position p21 as shown in Fig. 24. Until this point, since the second valve port 14Ih is shielded by the 20th straight portion 13Ih, no fluid flows out from the second valve port 14Ih.

[0068] After that, when the valve body assembly 13I is raised from position P21, as shown in Fig. 26, the first valve body 13Ic separates from the first valve port 14Ig, resulting in a flow rate change corresponding to the gap between the first valve port 14Ig and the 12th tapered portion 13Ig. On the other hand, since the second valve body 13Id is cylindrical, when the valve body assembly 13I is raised from position P21, the second valve port 14Ih is immediately opened. That is, the second valve body 13Id can cause a rapid flow rate change as shown from position p21 to position p22 in Fig. 24 because it fully opens or fully closes the second valve port 14Ih according to the position of the valve body assembly 13I.

[0069] (Fourth Embodiment) Figs. 27 to 30 are diagrams showing the valve body assembly 13K according to the fourth embodiment with different positions. In this embodiment, the valve body assembly 13K and the valve body 14K are different from those in the first embodiment. Since the other configurations are the same as those in the first embodiment, duplicate descriptions are omitted.

[0070] The valve body 14K is provided with a first outlet side flow path 14Kf communicating with the valve chamber 12 through the first valve port 14Kg and a second outlet side flow path 14Kd communicating with the valve chamber 12 through the second valve port 14Kh. Fluid is supplied to the valve chamber 12 through a supply path (not shown).

[0071] As shown in Fig. 27, the valve body assembly 13K is provided with a circular flange portion 13Ka and a shaft portion 13Kb connected to the center of the upper surface of the flange portion 13Ka. Since the flange portion 13Ka and the shaft portion 13Kb are the same as those in the first embodiment, duplicate descriptions are omitted.

[0072] On the lower surface of the flange portion 13Ka, a first valve body 13Kc is formed facing the first valve port 14Kg, and a second valve body 13Kd is formed facing the second valve port 14Kh.

[0073] The first valve body 13Kc includes, from the flange portion 13Ka side, a first straight portion 13Ks having a cylindrical shape with a smaller diameter than the first valve port 14Kg, an eleventh tapered portion (negative tapered portion) 13Kt that expands in diameter downward, a twelfth straight portion 13Ku having a short cylindrical shape, a thirteenth tapered portion (positive tapered portion) 13Kv that contracts in diameter downward, and a fourteenth tapered portion (positive tapered portion) 13Kw having a larger taper angle than the thirteenth tapered portion 13Kv, which are connected in series. The outer diameter of the twelfth straight portion 13Ku is equal to the inner diameter of the first valve port 14Kg. The axis L1 of the first valve body 13Kc is parallel to the axis L.

[0074] The second valve body 13Kd has only a cylindrical second straight portion 13Kh. The outer diameter of the second straight portion 13Kh is equal to the inner diameter of the second valve port 14Kh. The axis L2 of the second valve body 13Kd is parallel to the axis L.

[0075] (Application Example of the Fourth Embodiment) Hereinafter, a preferred application example of the electric drive valve according to the fourth embodiment will be described. Figs. 31 to 33 are schematic diagrams showing the refrigerant flow of a general heat pump type air conditioner capable of cooling, heating, and heating with dehumidification. In Figs. 31 to 33, two expansion valves EXV1 and EXV2 are used, and two solenoid valves SV1 and SV2 are used. Further, solid lines indicate that the refrigerant flow is allowed, and broken lines indicate that the refrigerant flow is blocked. Fig. 34 shows a table indicating the open / close states (Open / Close) and flow rate control states (Control) of the expansion valves EXV1 and EXV2 and the solenoid valves SV1 and SV2.

[0076] (Cooling) During cooling operation, as shown in Fig. 34, the expansion valves EXV1 and EXV2 are in the open state, and the solenoid valves SV1 and SV2 are in the closed state. As shown in Fig. 31, the refrigerant from the accumulator 100 is compressed by the compressor 101. The compressed refrigerant, which has become high-temperature and high-pressure, passes through the fully open expansion valve EXV1 and then through the condenser 103, where the liquefaction of the refrigerant is promoted. When passing through the expansion valve EXV2, throttling control is performed, and when passing through the evaporator 104, the vaporization of the refrigerant is promoted. Cooling is achieved by utilizing the heat exchange at this time. Subsequently, in the accumulator 100, gas-liquid separation of the refrigerant is carried out, and the gaseous-phase refrigerant heads towards the compressor 101. The adjustment of the cooling temperature is performed by adjusting the flow rate of the refrigerant passing through the expansion valve EXV2.

[0077] (Heating) During heating operation, as shown in Fig. 34, the expansion valve EXV1 and the solenoid valve SV2 are in the open state, and the expansion valve EXV2 and the solenoid valve SV1 are in the closed state. As shown in Fig. 32, the refrigerant from the accumulator 100 is compressed by the compressor 101. The compressed refrigerant, which has become high-temperature and high-pressure, releases condensation heat in the heat pump condenser 102 and changes into a medium-temperature and high-pressure refrigerant. Heating is achieved by utilizing the heat exchange at this time. Subsequently, the refrigerant becomes a low-temperature and low-pressure refrigerant after passing through the expansion valve EXV1, and its vaporization is promoted when passing through the condenser 103. Then it passes through the solenoid valve SV2, and gas-liquid separation of the refrigerant is carried out in the accumulator 100, and the gaseous-phase refrigerant heads towards the compressor 101. The adjustment of the heating temperature is performed by adjusting the flow rate of the refrigerant passing through the expansion valve EXV1.

[0078] (Heating and dehumidifying) During heating and dehumidification, as shown in Fig. 34, the expansion valves EXV1 and EXV2 and the solenoid valve SV1 are in the open state, and the solenoid valve SV2 is in the closed state. As shown in Fig. 33, the refrigerant from the accumulator 100 is compressed by the compressor 101. The compressed refrigerant becomes high-temperature and high-pressure, and the condensation heat is released by the heat pump condenser 102, changing into a medium-temperature and high-pressure refrigerant. Heating is performed by utilizing the heat exchange at this time. Then, after passing through the expansion valve EXV1, the refrigerant passes through the condenser 103 to promote the liquefaction of the refrigerant, and after passing through the expansion valve EXV2, the refrigerant passes through the evaporator 104 to promote the vaporization of the refrigerant. Dehumidification is performed by utilizing the heat exchange at this time. Then, in the accumulator 100, the gas-liquid separation of the refrigerant is performed, and the gaseous refrigerant goes towards the compressor 101. The adjustment of the heating temperature is performed by adjusting the flow rate of the refrigerant passing through the expansion valve EXV1, and the adjustment of dehumidification is performed by adjusting the flow rate of the refrigerant passing through the expansion valve EXV2.

[0079] Thus, in a general heat pump type air conditioner, in order to perform cooling, heating, and heating with dehumidification, the expansion valves EXV1 and EXV2 and the solenoid valves SV1 and SV2 are required. On the other hand, the electric drive valve 10K (shown by a dotted line in Figs. 31 to 33) according to the fourth embodiment can replace the expansion valve EXV1 and the solenoid valve SV1. This will be specifically described below.

[0080] In Figs. 27 to 30, it is assumed that the outlet of the heat pump condenser 102 is connected to the valve chamber 12, the first outlet side flow path 14Kf is connected to the inlet of the condenser 103, and the second outlet side flow path 14Kd is connected to the inlet of the expansion valve EXV2. Also, it is assumed that the axial movement control of the valve body assembly 13K is performed by a control device (not shown).

[0081] During cooling operation, the valve body assembly 13K is axially positioned within the range shown in FIGS. 27 to 28, with the upper and lower limits defined thereby. At this time, a first straight portion 13Ks is disposed inside the first valve port 14Kg, and the second valve port 14Kh is shielded by the second straight portion 13Kh. Therefore, except at the fully shielded position shown in FIG. 27, a predetermined amount of refrigerant passing through the gap between the first valve port 14Kg and the first straight portion 13Ks flows toward the condenser 103 regardless of the position of the valve body assembly 13K. The cooling temperature is adjusted by the expansion valve EXV2. However, the refrigerant flows toward the expansion valve EXV2 via the condenser 103 (see FIG. 31).

[0082] During heating operation, the valve body assembly 13K moves axially within the range shown in FIGS. 28 to 29. At this time, an eleventh tapered portion 13Kt is disposed inside the first valve port 14Kg, and the second valve port 14Kh is shielded by the second straight portion 13Kh. Therefore, the flow rate of the refrigerant passing through the gap between the first valve port 14Kg and the eleventh tapered portion 13Kt and flowing toward the condenser 103 changes according to the position of the valve body assembly 13K. Thereby, the heating temperature can be adjusted (see FIG. 32).

[0083] During heating and dehumidifying operation, the valve body assembly 13K moves axially within the range shown in FIGS. 29 to 30. At this time, a thirteenth tapered portion 13Kv or a fourteenth tapered portion 13Kw is disposed inside the first valve port 14Kg, and the second straight portion 13Kh retracts from the second valve port 14Kh. Therefore, the flow rate of the refrigerant passing through the gap between the first valve port 14Kg and the thirteenth tapered portion 13Kv or the fourteenth tapered portion 13Kw and flowing toward the condenser 103 changes according to the position of the valve body assembly 13K. Thereby, the heating temperature can be adjusted. In parallel with this, the refrigerant flows toward the expansion valve EXV2 (see FIG. 33). The dehumidifying adjustment is performed by EXV2.

[0084] According to the fourth embodiment, two valve devices having different functions can be replaced by a single electrically driven valve 10K, contributing to cost reduction of the air conditioner.

[0085] (Other Modifications) FIG. 35 is a cross-sectional view showing an enlarged view of the vicinity of a second valve port 14Kh according to a modification of the above-described embodiment. In this modification, an annular seal member 21 made of resin is disposed on the inner periphery of the second valve port 14Kh. The inner periphery of the annular seal member 21 is in contact with the outer peripheral surface of the 20th straight portion 13Kh, whereby the gap between the second valve port 14Kh and the 20th straight portion 13Kh is sealed, and leakage of the refrigerant is suppressed. Note that a flat seal member may be disposed between the flange portion and the bottom wall (around the valve port) of the middle main body portion to suppress fluid leakage in a fully closed valve state.

[0086] However, the present invention is not limited to the above embodiments. For example, in the valve body, a second valve port may be formed in an annular belt shape around the first valve port into which the first valve body is inserted, and the second valve body of the valve body assembly may be formed into a tubular shape surrounding the first valve body and inserted into the second valve port. At this time, by making the thickness of the second valve body thinner toward the tip, the flow rate of the fluid passing through the second valve port changes according to the axial position of the valve body assembly. According to such an example, an opening / closing valve operation can be performed regardless of the relative rotational direction position between the valve body and the valve body assembly, and it is not necessary to provide a guide. Needless to say, various modifications can be made to the above-described embodiments without departing from the gist of the present invention.

[0087] The fluid using the valve device of the present invention is not limited to a refrigerant, and may be a gas such as air or a liquid such as water, and its operating pressure may be, for example, around 0.3 MPa.

Explanation of Reference Numerals

[0088] 10 Electrically Operated Valve 13 - 13K Valve Body Assembly 13c - 13Kc First Valve Body 13d - 13Kd Second Valve Body 13e - 13He Third Valve Body 14, 14D, 14E, 14K Valve Body 14g, 14Ig, 14Kg First Valve Port Second valve ports of 14h, 14Ih, and 14Kh Third valve port of 14i 16 Rotor 18 Stator coil 21 Annular seal body

Claims

A valve body having a first valve port communicating the valve chamber and the first flow path, and a second valve port communicating the valve chamber and the second flow path, A valve body assembly including a first valve body that can be inserted into the first valve port and a second valve body that can be inserted into the second valve port, The first valve body includes a tapered portion in which the area of a cross section perpendicular to the moving direction of the first valve body changes as it moves in the moving direction of the first valve body, The second valve body includes a cylindrical portion in which the area of a cross section perpendicular to the moving direction of the second valve body is uniform, By moving the valve body assembly, each valve body is simultaneously displaced with respect to each valve port, When at least the cylindrical portion is located in the second valve port, the tapered portion is located in the first valve port, A valve device characterized by this. Claim 2 The first valve body has a positive tapered portion in which the cross-sectional area in a direction perpendicular to the moving direction decreases as it moves in one direction of the moving direction of the valve body assembly, and a negative tapered portion in which the cross-sectional area in a direction perpendicular to the moving direction increases, The valve device according to claim 1, characterized by this. Claim 3 Having a cylindrical straight portion between the positive tapered portion and the negative tapered portion, The valve device according to claim 2, characterized by this. Claim 4 The lengths of the first valve body and the second valve body along the axial direction of the valve body assembly are different from each other, and the first valve body and the second valve body sequentially enter or separate from the valve port, The valve device according to any one of claims 1 to 3, characterized by this. Claim 5 Before the first valve body retreats from the first valve port, the second valve body retreats from the second valve port, The valve device according to claim 4, characterized by this.

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