Rotary type switching valve

Abstract

To obtain a rotary selector valve that can enhance a reinforcing effect of the wall of a low-pressure flow passage and suppress deformation of the wall caused by a pressure difference between the inside and outside.SOLUTION: A rotary selector valve 100 comprises a valve body 1, a valve seat portion 20 having four ports 20D, 20S, 20C, and 20E, and a main valve 3 provided rotatably around a central axis 6 that intersects with the valve seat portion 20 inside the valve body 1. The main valve 3 has a low-pressure passage 30L that brings two adjacent ports into communication with each other. The low-pressure flow passage 30L is provided with a reinforcing member 7 extending between an inner-diameter inner wall 34, which is the wall on the inner diameter side in a radial direction Y that intersects with the central axis 6, and an outer-diameter inner wall 33, which is the wall on the outer diameter side opposite to the inner diameter side. The reinforcing member 7 is in contact with the outer-diameter inner wall 33 by an outer diameter side portion 7b that has a predetermined width and extends along the opening edge of the low-pressure flow passage 30L.SELECTED DRAWING: Figure 3

Description

Technical Field

[0001] The present invention relates to a rotary switching valve.

Background Art

[0002] A rotary switching valve for switching a fluid flow path is known (see, for example, Patent Document 1). The valve body of the rotary switching valve described in Patent Document 1 is a synthetic resin molded product, has two valve passages, and the valve body rotates while the opening edge of the valve passage is in sliding contact with the valve seat portion, thereby switching the communication state between the four ports provided in the valve seat portion and the valve passage. In this valve body, one of the two valve passages is a high-pressure flow path, and the other is a low-pressure flow path. Since the pressure inside the valve chamber becomes high pressure, stress due to the pressure difference between the inside and outside acts on the wall of the low-pressure flow path.

[0003] As a means for reinforcing the wall against such stress, a reinforcing pin provided in the valve body of a slide-type switching valve is known (see, for example, Patent Document 2). The reinforcing pin is provided so as to cross the inside of a bowl-shaped recess serving as a valve passage formed inside a valve body having an elliptical dome portion.

Prior Art Documents

Patent Documents

[0004]

Patent Document 1

Patent Document 2

Summary of the Invention

Problems to be Solved by the Invention

[0005] However, while the bowl-shaped recess of the valve body of the aforementioned slide-type directional control valve is formed in an elongated oval shape that is long in the sliding direction, and its wall thickness is equal in the sliding direction and in the direction perpendicular to it, the two valve passages of a rotary-type directional control valve are each formed around the central axis of the valve body, so their wall thickness tends to differ, especially in the direction in which the central axis intersects. In other words, in the direction in which the central axis intersects, the wall thickness on the outer side in the intersecting direction, which is opposite the central axis side, tends to be relatively smaller than the wall thickness on the inner side in the intersecting direction, which is on the central axis side, due to the wall thickness around the central axis. Consequently, in the low-pressure passage of the two valve passages of a rotary-type directional control valve, the stress due to the pressure difference between the inside and outside becomes large on the wall on the outer side in the intersecting direction, and even if reinforcing pins, like those used in slide-type directional control valves, are used to reinforce it, there is a problem that a sufficient reinforcing effect on the wall on the outer side in the intersecting direction cannot be obtained.

[0006] The object of the present invention is to provide a rotary switching valve that can enhance the reinforcing effect of the wall of the low-pressure flow path and suppress wall deformation due to the pressure difference between the inside and outside. [Means for solving the problem]

[0007] To solve the aforementioned problems and achieve the objective, the rotary switching valve of the present invention comprises a valve body constituting a valve chamber, a valve seat portion having four ports opening into the valve chamber, and a valve element rotatably provided inside the valve body around a central axis intersecting the valve seat portion, wherein the valve element comprises a high-pressure flow path and a low-pressure flow path connecting two adjacent ports. Furthermore, a sealing surface that abuts against the valve seat portion from one side in the axial direction of the central axis and separates the inside of the high-pressure passage from the inside of the low-pressure passage, The low-pressure flow path is provided with a reinforcing member that extends from the inner diameter side wall on the central axis side in the direction of intersection with the central axis, to the outer diameter side wall on the opposite side of the inner diameter side, and the reinforcing member is in contact with at least the outer diameter side wall by an outer contact portion having a predetermined width that extends along the opening edge of the low-pressure flow path. The reinforcing member is positioned at a distance from the sealing surface to one side in the axial direction. It is characterized by the following:

[0008] According to the present invention, the reinforcing member can secure a contact area of ​​a predetermined width along the opening edge of the low-pressure flow path by an outer contact portion that contacts the outer diameter wall of the low-pressure flow path. Therefore, when stress due to the pressure difference between the inside and outside of the valve body acts on the outer diameter wall of the low-pressure flow path, this stress can be received by the outer contact portion, and the effect of stress can be suppressed by the reinforcing member over a predetermined range. In this way, the outer diameter wall, which tends to have a relatively smaller wall thickness compared to the inner diameter wall thickness and is prone to the above-mentioned large stress, can be easily reinforced with the reinforcing member. Thus, a rotary switching valve can be obtained that enhances the reinforcing effect of the wall of the low-pressure flow path and suppresses wall deformation due to the pressure difference between the inside and outside.

[0009] In this case, it is preferable that the width dimension of the reinforcing member on the outer diameter side is larger than the width dimension of the inner diameter side. With this configuration, in the low-pressure flow path, the reinforcing member can be in contact with the outer diameter side wall over a wider area (i.e., with a larger contact area) than the inner diameter side wall, by the difference in width dimension. Therefore, by increasing the reinforcing effect of the outer diameter side wall, the reinforcing effect of the reinforcing member on the wall of the low-pressure flow path can be enhanced.

[0010] Furthermore, it is preferable that the height dimension of the reinforcing member on the outer diameter side is greater than the height dimension of the inner diameter side. With this configuration, in the low-pressure flow path, the reinforcing member can be in contact with the outer diameter side wall over a wider area than the inner diameter side wall, by the difference in height dimension. Therefore, by increasing the reinforcing effect of the outer diameter side wall, the reinforcing effect of the reinforcing member on the wall of the low-pressure flow path can be enhanced.

[0011] Furthermore, the width dimension of the reinforcing member on the outer diameter side may be equal to the width dimension of the inner diameter side.

[0012] Furthermore, in at least the low-pressure channel among the high-pressure channel and the low-pressure channel, the circumference near the opening edge of the outer diameter wall may be longer than that of the inner diameter wall. In such a configuration, in the low-pressure channel, the circumference near the opening edge of the outer diameter wall is longer than that of the inner diameter wall. As a result, the outer diameter wall, which is susceptible to stress as described above, will have a larger area than the inner diameter wall, making the outer diameter wall even more susceptible to stress. However, with this configuration, the stress acting on the outer diameter wall can be received by the outer contact portion, making it easier to reinforce the outer diameter wall, which is prone to high stress, with a reinforcing member.

[0013] Furthermore, in at least the low-pressure channel among the high-pressure channel and the low-pressure channel, the inner diameter wall and the outer diameter wall may each have an arc shape extending around the central axis with their opening edges concentric.

[0014] Furthermore, it is preferable that, at the switching position of the valve body, the two ports connected by the low-pressure flow path and the reinforcing member do not overlap when viewed in the axial direction of the central axis. With this configuration, when the valve body is connecting the two ports, the reinforcing member does not overlap the ports in the axial direction of the central axis, thus preventing the reinforcing member from obstructing the fluid moving between the two ports. Therefore, it is possible to improve the reinforcing effect of the valve body while suppressing a decrease in fluid flow rate.

[0015] Furthermore, the reinforcing member has an inner diameter side portion that contacts the inner diameter side wall of the low-pressure flow path, an outer diameter side portion that contacts the outer diameter side wall of the low-pressure flow path, and a pair of side portions that extend from one end and the other end of the inner diameter side portion to one end and the other end of the outer diameter side portion, and the pair of side portions may be formed in an arc shape that widens from the inner diameter side to the outer diameter side. With such a configuration, the reinforcing member can be formed in a shape such as a ginkgo leaf shape or a fan shape using the inner diameter side portion, the outer diameter side portion and the pair of side portions.

[0016] Further, the reinforcing member has an inner diameter side portion that contacts the inner diameter side wall, an outer diameter side portion that contacts the outer diameter side wall, and a pair of side portions that extend from one end portion and the other end portion of the inner diameter side portion to one end portion and the other end portion of the outer diameter side portion. The pair of side portions may be formed linearly. According to such a configuration, the reinforcing member can be formed into, for example, a trapezoidal shape or the like with an inner diameter side portion, an outer diameter side portion, and a pair of side portions.

[0017] Further, at least one of the reinforcing member and the valve body is provided with a retaining portion extending in the crossing direction. When the reinforcing member is about to be displaced toward the valve seat portion side, the retaining portion preferably includes a portion that contacts the other of the reinforcing member and the Scroll in the axial direction. According to such a configuration, the retaining portion provided on at least one of the reinforcing member and the valve body contacts the other of the reinforcing member and the valve body in the axial direction, thereby restricting the displacement of the reinforcing member that is about to be displaced toward the valve seat portion side. Thereby, it is possible to prevent the reinforcing member from falling off toward the valve seat portion side. valve body

Effect of the Invention

[0018]

Brief Description of the Drawings

[0019] [Figure 1] Assembly sectional view of a rotary switching valve according to an embodiment of the present invention. [Figure 2] Cross-sectional view of the valve body. [Figure 3] Bottom view of the valve body. [Figure 4] Partial enlarged view of the valve body and the reinforcing member. [Figure 5] Bottom view of the valve body in the first modification. [Figure 6] Partial enlarged view of the valve body and the reinforcing member in the first modification. [Figure 7] (A) and (B) are perspective views of the reinforcing member in the second modification. [Figure 8] Partial enlarged view of the valve body and the reinforcing member in the second modification. [Figure 9] (A) to (D) are diagrams showing variations in the shape of the reinforcing member with a non-uniform width dimension. [Figure 10] (A) to (C) are diagrams showing variations in the shape of the reinforcing member with the same width dimensions at both ends. [Figure 11] (A) is a schematic diagram of a refrigeration cycle system showing the state during cooling operation, and (B) is a schematic diagram of a refrigeration cycle system showing the state during heating operation.

Embodiments for Carrying Out the Invention

[0020] Hereinafter, embodiments of the present invention will be described based on FIGS. 1 to 4 and FIG. 11. FIG. 1 is an assembled cross-sectional view of a rotary switching valve 100 according to an embodiment of the present invention. FIG. 2 is a cross-sectional view of the main valve 3 (valve body). FIG. 3 is a bottom view of the main valve 3. FIG. 4 is a partial enlarged view of the main valve 3 and the reinforcing member 7. FIG. 11(A) is a schematic diagram of a refrigeration cycle system showing the state during cooling operation, and FIG. 11(B) is a schematic diagram of a refrigeration cycle system showing the state during heating operation.

[0021] In the drawings, arrow X and arrow Y are directions perpendicular to each other. Arrow X is taken as the axial direction of the valve body 1 and the central axis 6, and is referred to as the "axial direction X". Also, one side in the axial direction X is referred to as "upper side X1" and the other side is referred to as "lower side X2". Further, the intersecting direction intersecting the axis X is indicated by arrow Y and is referred to as the "radial direction Y". And particularly on the side where the central axis 6 is located in the radial direction Y is taken as the "inner diameter side", and the opposite side of the inner diameter side is taken as the "outer diameter side". This is for the convenience of explanation only and does not necessarily coincide with the direction in the actual use state of the rotary switching valve 100, and does not limit the direction in the actual use state of the rotary switching valve 100.

[0022] The rotary switching valve 100 comprises a valve body 1, a valve seat member 2, a main valve 3 (valve body), an auxiliary valve 4, a drive unit 5, a central shaft 6, and a reinforcing member 7. The valve body 1 comprises a cylindrical first cylindrical portion 10 extending in the axial direction X, and a bottomed cylindrical second cylindrical portion 11 that is continuous with the first cylindrical portion 10 and has a smaller diameter than the first cylindrical portion 10, and houses the main valve 3, auxiliary valve 4, drive unit 5, central shaft 6, and reinforcing member 7. The interior of the first cylindrical portion 10 constitutes a valve chamber 10a. The interior of the second cylindrical portion 11 constitutes a housing portion 11a that mainly houses the drive unit 5 and the like.

[0023] The valve seat member 2 comprises a cylindrical valve seat portion 20 and a flange portion 21 formed on the outer circumference of the valve seat portion 20. The valve seat portion 20 is fitted into the valve body 1 such that its outer surface is in contact with the inner surface of the first cylindrical portion 10, and its upper surface constitutes a valve seat surface 20a extending in the radial direction Y. As shown in Figure 3, the valve seat portion 20 is provided with four ports 20D, 20S, 20C, and 20E that penetrate from the lower end of the valve seat portion 20 to the valve seat surface 20a and open into the valve chamber 10a. Each of the ports 20D, 20S, 20C, and 20E opens at positions spaced 90° apart from each other.

[0024] The four ports consist of a D port 20D which communicates with the valve chamber 10a and the refrigerant discharge side of the compressor, an S port 20S which communicates with the refrigerant suction side of the compressor, a C switching port 20C which communicates with the outdoor heat exchanger side, and an E switching port 20E which communicates with the indoor heat exchanger side. Each of the ports 20D, 20S, 20C, and 20E is connected to a fitting pipe 8 (shown only in Figure 1) to form a refrigerant flow path. The flange portion 21 is fixed to the valve body 1 by welding with its upper surface in contact with the lower end surface of the first cylindrical portion 10.

[0025] The main valve 3 is a component made of resin and is installed inside the valve body 1 so as to be rotatable about a central axis 6 and displaceable in the direction of the axis X. As shown in Figure 2, the main valve 3 comprises a bowl portion 30 and a cylindrical piston portion 31 that extends upward X1, continuous with the bowl portion 30. The bowl portion 30 has a low-pressure passage 30L and a high-pressure passage 30H that open toward the valve seat surface 20a, and a pressure equalization hole 30a that communicates with the housing portion 11a from the ceiling of the low-pressure passage 30L.

[0026] The low-pressure passage 30L is a valve passage that connects two adjacent ports from the aforementioned ports 20D, 20S, 20C, and 20E, and is located opposite the high-pressure passage 30H across the central axis 6. The low-pressure passage 30L is provided with a rib 32 that protrudes downward X2 from its opening edge, and the lower end surface of the rib 32 constitutes a sealing surface 32a. As shown in Figure 1, the sealing surface 32a is capable of sliding against the valve seat surface 20a, and two of the four ports 20D, 20S, 20C, and 20E are connected by a space enclosed by the sealing surface 32a and the valve seat surface 20a, separated from the valve chamber 10a.

[0027] As shown in Figure 3, in the low-pressure flow path 30L, the outer diameter inner wall 33, which is the outer diameter side wall in the radial direction Y, and the inner diameter inner wall 34, which is the inner diameter side wall in the radial direction Y, are each formed in an arc shape that extends concentrically around the central axis 6 near the opening edge. The outer diameter inner wall 33 has a longer circumference near its opening edge compared to the inner diameter inner wall 34. As shown in Figure 2, the outer diameter inner wall 33 has a groove-shaped first stopper portion 33a that is recessed on the radial direction Y outer diameter side. The first stopper portion 33a has a predetermined width along the opening edge of the low-pressure flow path 30L and is formed extending upward X1 from the opening edge.

[0028] The inner diameter wall 34 has a groove-shaped second stopper portion 34a that is recessed towards the radial Y inner diameter side. The second stopper portion 34a has a predetermined width smaller than the first stopper portion 33a and is formed along the opening edge of the low-pressure flow path 30L, extending upward X1 from the opening edge.

[0029] In this configuration, because the main valve 3 has material (resin) around the central axis 6, the thickness of the outer diameter inner wall 33 tends to be relatively smaller than the thickness of the inner diameter inner wall 34 on the opposite side, making the outer diameter inner wall 33 more susceptible to stress caused by the pressure difference inside and outside the main valve 3. Therefore, a reinforcing member 7 is installed inside the low-pressure passage 30L, extending from the second stopper section 34a to the first stopper section 33a. In other words, the low-pressure passage 30L is provided with a reinforcing member 7 that extends across the inner diameter inner wall 34 and the outer diameter inner wall 33. A detailed explanation of the reinforcing member 7 will be given later.

[0030] The high-pressure passage 30H is a valve passage that connects two adjacent ports from among the ports 20D, 20S, 20C, and 20E. The lower end of this high-pressure passage 30H is positioned above X1 above the sealing surface 32a of the rib 32. Furthermore, in the cross-sectional view in Figure 2, the high-pressure passage 30H has a notch 30H1 formed from the outer diameter wall in the radial direction Y toward the inner diameter in the radial direction Y. As a result, the high-pressure passage 30H is a normally open space that is not separated from the valve chamber 10a.

[0031] A pair of sliding ribs 30b protruding downward X2 are formed on the bottom surface of the bowl portion 30. As shown in Figure 3, the sliding ribs 30b are formed at circumferential intervals on the semicircular portion of the bottom surface of the bowl portion 30 on the side where the high-pressure flow path 30H is formed. The lower end surface of the sliding ribs 30b is in the same position as the sealing surface 32a in the axial direction X, thereby preventing the main valve 3 from tilting toward the high-pressure flow path 30H when the sealing surface 32a and the valve seat surface 20a are in contact.

[0032] As shown in Figure 1, the piston portion 31 is formed such that a piston ring R is fitted around it, and the piston ring R slides against the inner circumferential surface of the second cylindrical portion 11 when the main valve 3 is displaced in the axial direction X. A cylindrical recess opening to the upper side X1 is formed in the center of the piston portion 31, and this recess constitutes an auxiliary valve housing chamber 31a that houses the auxiliary valve 4.

[0033] A sub-valve stopper 31a1 is formed on the inner circumferential surface of the sub-valve housing chamber 31a, projecting radially inward in the Y direction and extending in the axial direction X. A main valve projection 31a2 is formed on the bottom surface of the sub-valve housing chamber 31a, convex upward X1 on the circumference around the axial direction X. The upper X1 end of the aforementioned pressure equalization hole 30a is open into this main valve projection 31a2. The central part of the bottom surface of the sub-valve housing chamber 31a constitutes the bearing part of the central shaft 6, and a shaft insertion hole 3a is formed in the center of this bearing part, penetrating along the axial direction X to the lower end of the bowl part 30. The lower portion 6b of the central shaft 6, which will be described later, is inserted into the shaft insertion hole 3a. This supports the main valve 3 so that it can rotate around the central shaft (around axis X) and be displaced in the direction of axis X between the first switching position (switching position, shown in Figure 11(A)) and the second switching position (switching position, shown in Figure 11(B)), where it contacts the stop pin 9 (shown only in Figures 11(A) and (B)), which will be described later.

[0034] The auxiliary valve 4, like the main valve 3, is provided to be rotatable around the central axis 6 and displaceable in the axial direction X. The auxiliary valve 4 comprises a substantially semicircular flange portion 40 housed in the auxiliary valve housing chamber 31a, and a boss portion 41 formed in the center of the flange portion 40 and extending in the axial direction X. The radially outward Y end of the flange portion 40 is positioned to come into contact with the auxiliary valve stopper 31a1 when the auxiliary valve 4 rotates around the central axis 6 while the main valve 3 is in contact with the stop pin 9 and its rotation is restricted in the first or second switching position. This contact restricts the rotation of the auxiliary valve 4 around the central axis 6.

[0035] Multiple sub-valve protrusions 40a are formed on the lower surface of the flange portion 40, on the same circumference as the main valve protrusion 31a2 and protruding downward X2. The sub-valve protrusions 40a are formed spaced apart around the axis X so that two of them can sandwich one main valve protrusion 31a2. The lower end surface of the sub-valve protrusions 40a constitutes a sealing surface 40a1 that seals the aforementioned pressure equalization hole 30a. On the lower surface of the flange portion 40, a pressure equalization passage (not shown) is formed between two sub-valve protrusions 40a, which is able to communicate with the pressure equalization hole 30a. Therefore, when the sealing surface 40a1 of the sub-valve protrusions 40a seals the pressure equalization hole 30a, the high-pressure valve chamber 10a and the low-pressure passage 30L are separated. However, when the pressure equalization passage and the pressure equalization hole 30a are in communication, the pressure in the low-pressure passage 30L and the valve chamber 10a becomes uniform.

[0036] A rectangular hole 41a is formed in the center of the boss portion 41, opening to the upper side X1, into which the cam portion 50a of the worm wheel 50, which will be described later, is fitted. At the center of the bottom of the rectangular hole 41a, a shaft insertion hole 4a is formed, penetrating through to the lower end of the flange portion 40 along the axis X direction. The upper portion 6a of the central shaft 6, which will be described later, is inserted into the shaft insertion hole 4a, thereby supporting the sub-valve 4 so that it can rotate around the central shaft 6 and be displaced in the axis X direction.

[0037] The drive unit 5 includes a worm wheel 50 rotatably mounted on a central shaft 6 and a worm gear 51 meshed with the worm wheel 50. The worm wheel 50 has a cam portion 50a protruding downward X2, and is rotatably mounted on the central shaft 6 by the cam portion 50a. The cam portion 50a is fitted into the square hole 41a of the auxiliary valve 4. As a result, the auxiliary valve 4 and the worm wheel 50 become one unit and cooperate to rotate together around the axis X. A coil spring 52 is positioned between the worm wheel 50 and the auxiliary valve 4 to bias the auxiliary valve 4 downward X2. The worm gear 51 is fixed to the drive shaft of a motor (not shown).

[0038] The central shaft 6 is a main shaft extending in the direction of the axis X. The central shaft 6 comprises an upper portion 6a that is inserted through the center of the worm wheel 50 and the shaft insertion hole 4a of the auxiliary valve 4, and a lower portion 6b that is formed to be smaller in diameter than the upper portion 6a and is inserted through the shaft insertion hole 3a of the main valve 3. A ball B is fixed to the upper end of the upper portion 6a by crimping an annular rim, and the upper portion 6a is supported by a bearing groove provided in the center of the ceiling wall of the second cylindrical portion 11 of the valve body 1 via this ball B. The lower end of the lower portion 6b is supported by a bearing groove provided in the center of the valve seat portion 20 of the valve seat member 2. A washer 61 is fitted in the continuous portion between the upper portion 6a and the lower portion 6b, and the force when the main valve 3 rises upward X1 is transmitted to the central shaft 6 via this washer 61.

[0039] As described above, the reinforcing member 7 is a member that extends across the inner diameter inner wall 34 and the outer diameter inner wall 33 of the low-pressure flow path 30L. The reinforcing member 7 functions as a beam that reinforces the main valve 3 and is installed to prevent deformation of the main valve 3.

[0040] The reinforcing member 7 is formed in the shape of a plate from a metal material such as stainless steel, brass, aluminum, and copper, or from resin. This reinforcing member 7 comprises an inner diameter side portion 7a that contacts the inner diameter wall 34 (the wall on the radially Y inner diameter side of the low-pressure flow path 30L), an outer diameter side portion 7b that contacts the outer diameter wall 33 (the wall on the radially Y outer diameter side of the low-pressure flow path 30L), and a pair of side portions 7c that extend from one end and the other end of the inner diameter side portion 7a to one end and the other end of the outer diameter side portion 7b.

[0041] The inner diameter side portion 7a has a shape in which the end face on the radially Y inner diameter side conforms to the radially Y outer diameter side surface of the second contact portion 34a of the inner diameter inner wall 34, and is fixed by press-fitting so as to abut against the radially Y outer diameter side surface of the second contact portion 34a. The outer diameter side portion 7b has a shape in which the end face on the radially Y outer diameter side conforms to the radially Y outer diameter side surface of the first contact portion 33a of the outer diameter inner wall 33, and is fixed by press-fitting so as to abut against the radially Y outer diameter side surface of the first contact portion 33a.

[0042] As described above, the outer diameter inner wall 33 forms an outer contact portion that extends in an arc shape along the first contact portion 33a, which is wider than the second contact portion 34a. In other words, the width dimension of the reinforcing member 7 on the radial Y outer diameter side is set to be larger than the width dimension on the inner diameter side. Furthermore, the reinforcing member 7 is in contact with at least the outer diameter inner wall 33 by an outer contact portion having a predetermined width that extends along the opening edge.

[0043] The pair of side portions 7c are formed in an arc shape such that the width dimension of the reinforcing member 7 increases from the inner diameter side to the outer diameter side in the radial direction Y. In other words, the pair of side portions 7c are formed in an arc shape that widens from the inner diameter side to the outer diameter side. As a result, the reinforcing member 7 is formed in a ginkgo leaf shape or a fan shape when viewed from below in Figure 3.

[0044] Furthermore, the reinforcing member 7 configured in this way is positioned such that, in the first or second switching position where the main valve 3 connects ports 20E, 20S, 20D, and 20C, the two ports connected by the low-pressure flow path 30L (in Figure 3, the E switching port 20E and the S port 20S) and the reinforcing member 7 do not overlap when viewed in the direction of the axis X of the central axis 6.

[0045] Next, the operation of the main valve 3 and the sub-valve 4 will be explained. First, as shown in Figure 11(A), the drive unit 5 operates from the first switching position in which the low-pressure passage 30L of the main valve 3 connects the E switching port 20E and the S port 20S, and the high-pressure passage 30H connects the D port 20D and the C switching port 20C. When this happens, the driving force of the worm gear 51 and the worm wheel 50 is transmitted to the sub-valve 4 via the cam portion 50a, causing the sub-valve 4 to rotate around axis X (counterclockwise).

[0046] In this case, the sealing surface 40a1 of the auxiliary valve projection 40a and the upper surface of the main valve projection 31a2 are in contact as shown in Figure 1, so the pressure equalization hole 30a opening into the main valve projection 31a2 is closed by the sealing surface 40a1. Therefore, the main valve 3 is pressed against the valve seat 20 due to the pressure difference between the inside and outside, and even if the auxiliary valve 4 rotates, the main valve 3 cannot rotate due to the frictional force with the valve seat 20, and only the auxiliary valve 4 rotates.

[0047] When the sub-valve 4 rotates, the sub-valve projection 40a slides on the main valve projection 31a2, and the pressure equalization hole 30a opens through a pressure equalization passage (not shown) formed between the two sub-valve projections 40a on the lower surface of the flange portion 40 of the sub-valve 4. As a result, the fluid pressure on the upper side X1 outside the main valve 3 escapes into the low-pressure passage 30L (low-pressure side). The main valve projection 31a2 then moves to a position where it is sandwiched between the two sub-valve projections 40a, and the main valve projection 31a2 and the two sub-valve projections 40a interlock. In this state, the pressure is equalized between the upper side X1 of the main valve 3 and the low-pressure passage 30L, so as described above, the force pressing the main valve 3 against the valve seat portion 20 decreases, and the frictional force between the main valve 3 and the valve seat portion 20 becomes smaller than the interlocking force between the main valve projection 31a2 and the two sub-valve projections 40a.

[0048] Therefore, by rotating the sub-valve 4 around axis X, the main valve protrusion 31a2 and the sub-valve protrusion 40a come into contact with each other and rotate together around axis X. As a result, as shown in Figure 11(B), the main valve 3 moves to the second switching position in which the low-pressure passage 30L connects the C switching port 20C and the S port 20S, and the high-pressure passage 30H connects the D port 20D and the E switching port 20E. At this time, the wall of the high-pressure passage 30H comes into contact with the stop pin 9, which restricts the main valve 3 from rotating further around axis X.

[0049] If the sub-valve 4 is further rotated around axis X in this state, only the sub-valve 4, whose rotation is not restricted, will rotate around axis X until it comes into contact with the sub-valve stopper 31a1. As a result, the sub-valve protrusion 40a rides up onto the main valve protrusion 31a2, and the pressure equalization hole 30a is closed by the sealing surface 40a1. Therefore, the high-pressure fluid cannot escape from the pressure equalization hole 30a into the low-pressure flow path 30L, causing the upper side X1 outside the main valve 3 to become high-pressure, and the pressure difference between the upper side X1 of the main valve 3 and the low-pressure flow path 30L presses the main valve 3 against the valve seat 20.

[0050] Next, a refrigeration cycle system using a rotary switching valve 100 as a flow path switching valve will be described. Figure 11 is a diagram showing a refrigeration cycle system of an embodiment, and is an example of a refrigeration cycle system for an air conditioner. The air conditioner has a compressor P, an outdoor heat exchanger 60 (condenser or evaporator), an expansion valve 70, an indoor heat exchanger 80 (condenser or evaporator), and a rotary switching valve 100 as a flow path switching valve. Each of these elements is connected by conduits as shown in the figure, forming a heat pump type refrigeration cycle system.

[0051] The flow path of the refrigeration cycle system can be switched between two flow paths, cooling operation and heating operation, by rotating the main valve 3 of the rotary switching valve 100 as described above. In cooling operation as shown in Figure 11(A), the S port 20S is connected to the E switching port 20E by the low-pressure flow path 30L of the main valve 3 of the rotary switching valve 100, and the D port 20D is connected to the C switching port 20C by the high-pressure flow path 30H. As shown by the arrows in the figure, the refrigerant, as a fluid compressed by the compressor P, flows into the D port 20D of the rotary switching valve 100 and flows into the outdoor heat exchanger 60 from the C switching port 20C, and the refrigerant flowing out of the outdoor heat exchanger 60 flows into the expansion valve 70. The refrigerant is then expanded in the expansion valve 70 and supplied to the indoor heat exchanger 80. The refrigerant flowing out of the indoor heat exchanger 80 flows from the E switching port 20E to the S port 20S via the rotary switching valve 100, and is then circulated from the S port 20S to the compressor P.

[0052] During heating operation as shown in Figure 11(B), the rotary switching valve 100 connects the S port 20S to the C switching port 20C via the low-pressure flow path 30L of the main valve 3, and connects the D port 20D to the E switching port 20E via the high-pressure flow path 30H. As indicated by the arrows in the figure, the refrigerant compressed by the compressor P flows into the D port 20D of the rotary switching valve 100 and flows into the indoor heat exchanger 80 from the E switching port 20E. The refrigerant flowing out of the indoor heat exchanger 80 flows into the expansion valve 70. The refrigerant is then expanded in the expansion valve 70 and supplied to the outdoor heat exchanger 60. The refrigerant flowing out of the outdoor heat exchanger 60 flows from the C switching port 20C to the S port 20S in the rotary switching valve 100, and is circulated from the S port 20S back to the compressor P.

[0053] As described above, according to this embodiment, the reinforcing member 7 can secure a contact area of ​​a predetermined width along the opening edge of the low-pressure flow path 30L by its outer diameter side portion 7b (outer contact portion) that contacts the outer diameter inner wall 33 (outer diameter side wall) of the low-pressure flow path 30L. Therefore, when stress due to the pressure difference between the inside and outside of the main valve 3 (valve body) acts on the outer diameter inner wall 33 of the low-pressure flow path 30L, that stress can be received by the outer diameter side portion 7b, and the effect of stress can be suppressed by the reinforcing member 7 over a predetermined range. In this way, the outer diameter inner wall 33, which tends to have a relatively smaller wall thickness compared to the inner diameter side wall thickness and is prone to the above-mentioned large stress, can be easily reinforced with the reinforcing member 7. Therefore, a rotary switching valve 100 can be obtained that enhances the reinforcing effect of the wall of the low-pressure flow path 30L and suppresses wall deformation due to the pressure difference between the inside and outside.

[0054] Furthermore, since the width dimension of the outer diameter side portion 7b is larger than the width dimension of the inner diameter side portion 7a, in the low-pressure flow path 30L, the reinforcing member 7 can be in contact with the outer diameter inner wall 33 over a wider area (i.e., with a larger contact area) than the inner diameter inner wall 34, by the difference in width dimension. Therefore, by increasing the reinforcing effect of the outer diameter inner wall 33, the reinforcing effect of the reinforcing member 7 on the wall of the low-pressure flow path 30L can be enhanced.

[0055] In the low-pressure flow path 30L as in this embodiment, the circumference near the opening edge of the outer diameter inner wall 33 is longer than the circumference near the opening edge of the inner diameter inner wall 34. As a result, the area of ​​the outer diameter inner wall 33 is larger than the area of ​​the inner diameter inner wall 34, and the outer diameter inner wall 33 (outer diameter side wall), which is susceptible to stress as described above, becomes even more susceptible to stress. However, with the above configuration, the stress acting on the outer diameter inner wall 33 can be received by the outer diameter side portion 7b, making it easier to reinforce the outer diameter inner wall 33, which is prone to high stress, with the reinforcing member 7.

[0056] Furthermore, when the main valve 3 is connecting two ports, the reinforcing member 7 does not overlap with the central axis 6 in the direction of the axis X relative to the port. Therefore, it is possible to suppress the reinforcing member 7 from obstructing the fluid moving between the two ports. Consequently, it is possible to improve the reinforcing effect of the main valve 3 while suppressing a decrease in fluid flow rate.

[0057] Furthermore, according to this embodiment, the reinforcing member 7 can be formed in the shape of a ginkgo leaf or a fan, etc., by having an inner diameter side portion 7a, an outer diameter side portion 7b, and a pair of side portions 7c.

[0058] Furthermore, a rotary-type switching valve 100, which enhances the reinforcing effect of the wall of the low-pressure flow path 30L and suppresses wall deformation due to the pressure difference between the inside and outside, can be used as the flow path switching valve to configure the refrigeration cycle system.

[0059] Next, a first modified example of the rotary type switching valve 100 will be described. Figure 5 is a bottom view of the main valve 3 in the first modified example. Figure 6 is a partially enlarged view of the main valve 3 and the reinforcing member 7 in the first modified example. In the first modified example, the shape of the first stopper portion 33a differs from that of the embodiment described above. The first stopper portion 33a is formed only in the portion that contacts one end and the other end in the width direction of the outer diameter side portion 7b of the reinforcing member 7. It is preferable that the curvature of the surface on the radial Y outer diameter side of this first stopper portion 33a be formed with a curvature that is slightly larger than the curvature of the portion of the outer diameter side portion 7b that it contacts. With this configuration, both ends in the width direction of the outer diameter side portion 7b can be reliably brought into contact with the first stopper portion 33a, making it easier to reinforce the area from one end to the other end in the width direction of the outer diameter side portion 7b with respect to the outer diameter inner wall 33 using the reinforcing member 7.

[0060] Specifically, the outer diameter inner wall 33 can be supported at at least two points with a gap between them, covering the area from one end to the other in the width direction of the outer diameter side portion 7b. Compared to the conventional configuration where a single point is supported by a reinforcing pin, this configuration allows for support over a wider area by the reinforcing member 7, distributing the stress on the outer diameter inner wall 33 and reducing the range over which the outer diameter inner wall 33 can deform.

[0061] Furthermore, this configuration is preferable because, even if dimensional tolerances occur in the outer diameter side portion 7b or the first contact portion 33a, both ends of the outer diameter side portion 7b in the width direction will reliably contact the first contact portion 33a, thereby reducing the risk that only the central part of the outer diameter side portion 7 in the width direction will make point contact with the first contact portion 33a.

[0062] Furthermore, with this configuration, as shown in Figure 6, the width dimension W of the portion of the outer diameter side portion 7b of the reinforcing member 7 other than the portion that contacts one end and the other end in the width direction can be made larger compared to the above-described embodiment, thereby increasing the strength of the outer diameter inner wall 33.

[0063] Next, a second modified example of the rotary switching valve 100 will be described. Figures 7(A) and 7(B) are perspective views of the reinforcing member 7 in the second modified example. Figure 8 is a partially enlarged view of the main valve 3 and the reinforcing member 7 in the second modified example. In the second modified example, the shape of the reinforcing member 7 differs from that of the above-described embodiment and the first modified example. An inner diameter projection 7a1 (retaining part) is formed on the inner diameter side portion 7a of the reinforcing member 7, projecting toward the inner diameter in the radial direction Y. The inner diameter projection 7a1 is formed in a substantially triangular shape, with the width in the axial direction X decreasing towards the tip. In addition, a pair of outer diameter projections 7b1 (retaining parts) are formed on the outer diameter side portion 7b, projecting toward the outer diameter in the radial direction Y. The outer diameter projections 7b1 are formed in the same shape as the inner diameter projections 7a1 and are arranged on one end and the other end in the width direction of the outer diameter side portion 7b, respectively. These inner diameter projections 7a1 and outer diameter projections 7b1 are formed by press working, respectively. The inner diameter projection 7a1 and the outer diameter projection 7b1 facing downward X2 have surfaces (portions) that come into contact with the main valve 3 downward X2 when the reinforcing member 7 attempts to displace towards the valve seat portion 20, thereby causing the inner diameter projection 7a1 and the outer diameter projection 7b1 to function as retainers.

[0064] In the above-described embodiment and the first modified example, the reinforcing member 7 was fixed to the main valve 3 by press-fitting the outer diameter side portion 7b and the inner diameter side portion 7a, i.e., the end faces of the reinforcing member 7, into the first stopper portion 33a and the second stopper portion 34a, respectively. However, in the second modified example, the reinforcing member 7 can be firmly fixed to the main valve 3 by biting the outer diameter projection 7b1 and the inner diameter projection 7a1 into the first stopper portion 33a and the second stopper portion 34a, respectively. In this configuration, the depth of the grooves of the first stopper portion 33a and the second stopper portion 34a can be adjusted to bring the end faces of the outer diameter side portion 7b and the inner diameter side portion 7a into contact with the first stopper portion 33a and the second stopper portion 34a, in addition to the outer diameter projection 7b1 and the inner diameter projection 7a1, thereby fixing the reinforcing member 7 to the main valve 3.

[0065] With this configuration, both ends in the width direction of the outer diameter side portion 7b can be reliably brought into contact with the first stopper portion 33a by the outer diameter projection 7b1, making it easier to reinforce the area of ​​the outer diameter side portion 7b from one end to the other in the width direction with the reinforcing member 7 against the outer diameter inner wall 33. Furthermore, by engaging the inner diameter projection 7a1 with the second stopper portion 34a and the outer diameter projection 7b1 with the first stopper portion 33a, the reinforcing member 7 can be stably maintained in a fixed state with the main valve 3. In this case, the inner diameter projection 7a1 and the outer diameter projection 7b1 each function as retainers, preventing the reinforcing member 7 from coming loose due to vibration or fluid force.

[0066] Although not shown in the diagram, the retaining portion for preventing the reinforcing member 7 from coming loose may be provided on the main valve 3 side. For example, projections can be provided that protrude radially inward from the first contact portion 33a and the second contact portion 34a, and these can serve as the retaining portion. That is, the portion of the projection facing upward X1 will be the part that abuts the reinforcing member 7 toward upward X1 when the reinforcing member 7 attempts to displace toward the valve seat portion 20, and by bringing this into contact with the lower portion X2 of the reinforcing member 7, the reinforcing member 7 can be supported and prevented from coming loose toward downward X2 (valve seat portion 20 side).

[0067] With this configuration, the retaining portion (for example, an inner diameter projection 7a1 and an outer diameter projection 7b1) provided on at least one of the reinforcing member 7 and the main valve 3 abuts against the other of the reinforcing member 7 and the main valve 3 in the direction of axis X, thereby restricting the displacement of the reinforcing member 7 that would otherwise be displaced toward the valve seat portion 20. This prevents the reinforcing member 7 from falling out toward the valve seat portion 20.

[0068] Although embodiments and modifications of the present invention have been described in detail above with reference to the drawings, the specific configuration is not limited to these embodiments, and any design changes, etc., that do not depart from the spirit of the present invention are also included.

[0069] In this embodiment and its modifications, the reinforcing member 7 is formed in a flat plate shape as shown in Figure 2, but the shape of the reinforcing member 7 is not limited to this. For example, the height dimension of the side with the outer diameter side portion 7b (outer diameter side) of the reinforcing member 7 may be set to be larger than the height dimension of the side with the inner diameter side portion 7a (inner diameter side). This increases the contact area between the outer diameter side portion 7b, i.e., the outer contact portion, and the outer diameter inner wall 33, allowing more stress to be received by the outer contact portion, thereby further reducing the effects of stress. In this case, as a means of increasing the contact area by increasing the height dimension of the side with the outer diameter side portion 7b, the outer diameter side portion 7b may be simply made thicker, or the end of the outer diameter side of the outer diameter side portion 7b on the radial Y side may be bent in the axial X direction, i.e., either the upper side X1 or the lower side X2. In this case, the part that is made thicker or bent may be limited to only the side of the reinforcing member 7 that abuts against the inner wall which is susceptible to the aforementioned stress.

[0070] Furthermore, the reinforcing member 7 was formed in a flat plate shape as shown in Figure 2. However, the reinforcing member 7 may also be formed such that, for example, the side shape or cross-sectional shape of the reinforcing member 7, when viewed in the radial direction Y from the outer diameter side or inner diameter side as shown in Figure 7, curves in an arc towards either the upper side X1 or the lower side X2 in the axial direction X. With such a configuration, the reinforcing member 7 is less likely to buckle when pressure is applied in the radial direction Y compared to when it is formed in a flat plate shape, and is therefore preferable from the viewpoint of improving the strength of the reinforcing member 7. In addition, although the reinforcing member 7 was formed of metal or resin as described above, the material is not particularly limited, and any material may be used as long as it has rigidity and compatibility with refrigerants.

[0071] Furthermore, the reinforcing member 7 does not necessarily have to be formed in a ginkgo leaf shape or a fan shape, and may be formed in various shapes. Figures 9(A) to 9(D) show variations in the shape of the reinforcing member with an inconsistent width dimension. According to this, for example, as shown in Figure 9(D), the reinforcing member 7 has an inner diameter side portion 7a that contacts the inner diameter inner wall 34, an outer diameter side portion 7b that contacts the outer diameter inner wall 33, and a pair of side portions 7c that extend from one end and the other end of the inner diameter side portion 7a to one end and the other end of the outer diameter side portion 7b, and the pair of side portions 7c are formed in a straight line. That is, the reinforcing member 7 may be formed in a trapezoidal shape or the like with the inner diameter side portion 7a, the outer diameter side portion 7b, and the pair of side portions 7c.

[0072] Furthermore, in the low-pressure flow path 30L, the outer diameter inner wall 33, which is the outer diameter wall in the radial direction Y, and the inner diameter inner wall 34, which is the inner wall wall in the radial direction Y, do not necessarily have to be formed in a concentric arc shape extending around the central axis 6 near their opening edges, as shown in Figure 3. Also, in the low-pressure flow path 30L, the outer diameter inner wall 33, which is the outer diameter wall in the radial direction Y, does not necessarily have to have a longer circumference near its opening edge compared to the inner diameter inner wall 34, which is the outer diameter wall in the radial direction Y. In other words, the shape near the opening edge of the low-pressure flow path 30L may be an oval or an ellipse. The same applies to the high-pressure flow path 30H.

[0073] Furthermore, in the above-described embodiments and modifications, the second stopper portion 34a is formed to have a predetermined width smaller than the first stopper portion 33a along the opening edge of the low-pressure flow path 30L, and by providing a reinforcing member 7 with an irregular width within the low-pressure flow path 30L, the pressure resistance of the low-pressure flow path 30L, which is composed of inner walls of different areas (outer diameter inner wall 33 and inner diameter inner wall 34), is improved. However, if a sufficient reinforcing effect can be obtained, the predetermined widths of the first stopper portion 33a and the second stopper portion 34a may be set to be the same, and a reinforcing member 7 with the same width dimensions at both ends may be provided. Figures 10(A) to (C) show variations in the shape of the reinforcing member 7 with the same width dimensions at both ends. According to this, as shown in Figure 10(A), the reinforcing member 7 may be formed with a uniform width, or as shown in Figures 10(B) and (C), only the width dimensions at the ends of the reinforcing member 7 may be made the same. [Explanation of Symbols]

[0074] X axis Y radial direction (crossing direction) 1 Valve body 3. Main valve (valve body) 6 center axis 7 Reinforcement members 7b Outer diameter side (outer contact part) 10a Valve chamber 20 Valve seat 20E E switching port 20C C switching port 20D D-port 20S S-Port 30H High-pressure channel 30L Low-Pressure Flow Channel 34. Inner diameter inner wall (inner diameter side wall) 33. Outer diameter inner wall (outer diameter side wall) 100 Rotary-type switching valve

Claims

1. A rotary switching valve comprising a valve body constituting a valve chamber, a valve seat portion having four ports opening into the valve chamber, and a valve element rotatably mounted inside the valve body around a central axis intersecting the valve seat portion, The valve body has a high-pressure passage and a low-pressure passage that connect two adjacent ports, and a sealing surface that abuts against the valve seat from one side in the axial direction of the central axis and separates the interior of the high-pressure passage from the interior of the low-pressure passage. The low-pressure flow path is provided with a reinforcing member that extends from the inner diameter side wall, which is on the side of the central axis in the direction of intersection with the central axis, to the outer diameter side wall, which is on the opposite side of the inner diameter side. The reinforcing member is in contact with at least the outer diameter wall by an outer contact portion having a predetermined width that extends along the opening edge of the low-pressure flow path, The rotary switching valve is characterized in that the reinforcing member is arranged at a distance from the sealing surface on one side in the axial direction.

2. The rotary switching valve according to claim 1, characterized in that the width dimension on the outer diameter side of the reinforcing member is larger than the width dimension on the inner diameter side.

3. The rotary switching valve according to claim 1, characterized in that the height dimension on the outer diameter side of the reinforcing member is greater than the height dimension on the inner diameter side.

4. The rotary switching valve according to claim 1, characterized in that the reinforcing member has an outer diameter width dimension equal to the inner diameter width dimension.

5. The rotary switching valve according to claim 1, characterized in that in at least the low-pressure flow path among the high-pressure flow path and the low-pressure flow path, the circumference near the opening edge of the outer diameter wall is longer than that of the inner diameter wall.

6. The rotary switching valve according to claim 1, characterized in that, in at least the low-pressure flow path among the high-pressure flow path and the low-pressure flow path, the inner diameter side wall and the outer diameter side wall are concentric near the opening edge and have an arc shape extending around the central axis.

7. The rotary switching valve according to claim 1, characterized in that, at the switching position of the valve body, the two ports connected by the low-pressure flow path and the reinforcing member do not overlap when viewed in the axial direction of the central axis.

8. The rotary switching valve according to claim 1, wherein the reinforcing member has an inner diameter side portion that contacts the inner diameter side wall of the low-pressure flow path, an outer diameter side portion that contacts the outer diameter side wall of the low-pressure flow path, and a pair of side portions that extend from one end and the other end of the inner diameter side portion to one end and the other end of the outer diameter side portion, and the pair of side portions are formed in an arc shape that widens from the inner diameter side to the outer diameter side.

9. The rotary switching valve according to claim 1, wherein the reinforcing member has an inner diameter side portion that contacts the inner diameter side wall, an outer diameter side portion that contacts the outer diameter side wall, and a pair of side portions that extend from one end and the other end of the inner diameter side portion to one end and the other end of the outer diameter side portion, and the pair of side portions are formed in a straight line.

10. At least one of the reinforcing member and the valve body is provided with a retaining portion extending in the intersecting direction. The rotary switching valve according to claim 1, characterized in that the retaining portion has a portion that contacts the other of the reinforcing member and the valve body in the axial direction when the reinforcing member attempts to be displaced toward the valve seat portion.

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