Electric valve and refrigeration cycle system

Abstract

To provide a motor-operated valve that comprises speed reduction means for a fluid speed, thereby restrains fluid passage noise, and can enhance quietness, and a refrigeration cycle system comprising the same.SOLUTION: A motor-operated valve 100a comprises: a rotor part comprising a valve element 20A; a valve body 10A comprising a flow passage chamber 13, and a valve port 11a extending in a radial direction; and speed reduction means for reducing a speed of fluid passing through the valve port 11a. The valve body 10A comprises a guide part 11d for guiding the valve element 20A in a circumferential direction, a first port 1a directly communicating with the flow passage chamber 13, and a second port 2a directly communicating with the valve port 11a. A valve part 20a comprises a flow passage part 15 capable of communicating with the valve port 11a. In the speed reduction means, the valve element 20A or the guide part 11d comprises a wall surface part 20ga directly opposed to the first port 1a.SELECTED DRAWING: Figure 2

Description

[Technical Field]

[0001] The present invention relates to an electrically operated valve having a means for reducing the velocity of a fluid, and a refrigeration cycle system using the same. [Background technology]

[0002] When a motor-operated valve is used in a refrigeration cycle system, it may be disposed in an indoor unit of an air conditioner, and therefore there is a demand for improved quietness.

[0003] A typical motor-operated valve has a drive unit with a screw feed unit that converts rotary motion into linear motion, and a sliding unit that occurs between the valve element and a guide unit, which moves axially due to this linear motion. This causes momentary contact and separation, or collision, in the radial and axial directions in the screw feed unit, and the resulting vibrations and collisions are transmitted to the outside as operating noise (hereinafter referred to as "Conventional Problems (Noise from Motor-Operated Valves)").

[0004] In contrast, Patent Document 1 discloses an electrically operated valve (hereinafter referred to as a "conventional electrically operated valve") 900, as shown in FIG. 9(a), which includes a valve body 910, a valve element 920, and a stepping motor 930. The valve body 910 has a pair of valve ports 911a, a valve seat 911b, and a cylindrical guide portion 911c, and is connected to a first joint pipe 901 and a second joint pipe 902. The valve element 920 has a valve portion 920a, a bottomed cylindrical portion 920b slidably engaged with the outer periphery of the guide portion 911c, and a pair of circular openings 920f. The stepping motor 930 has a magnet rotor 932 that rotates integrally with the valve element 920.

[0005] For this reason, Patent Document 1 describes a configuration in which the bottomed cylindrical portion 920b can move only in the rotational direction relative to the guide portion 911c, thereby eliminating the need for a screw feed portion and suppressing the generation of operating noise in the drive portion.

[0006] However, in Patent Document 1, as shown in Figures 9(a) and (b), in the valve open state, the centers of a pair of valve ports 911a in a valve body 910 and a pair of circular openings 920f in a valve portion 920a are aligned on the same straight line. Therefore, the high-speed fluid flowing in from the first port 901a flows directly to the second port 902a through the valve port 911a without being decelerated. As a result, turbulence occurs when the fluid passes through the valve port 911a, causing pressure fluctuations to propagate as sound waves to the surrounding area, generating fluid passing noise. For this reason, Patent Document 1 still fails to solve the conventional problem (noise from motor-operated valves). [Prior art documents] [Patent documents]

[0007] [Patent Document 1] Japanese Patent Application Publication No. 9-4743 Summary of the Invention [Problem to be solved by the invention]

[0008] An object of the present invention is to provide an electrically operated valve that is equipped with a means for reducing the fluid velocity, thereby suppressing the noise generated by passing the fluid and improving quietness, and a refrigeration cycle system using the same. [Means for solving the problem]

[0009] In order to solve the above problems, there is provided a valve body including a valve element having a valve portion provided on one end side thereof, a rotor portion having a rotor that rotates integrally with the valve element, a flow path chamber that houses the valve portion, a valve seat that faces the valve portion in the radial direction, and a valve port that extends in the radial direction so as to be able to communicate with the flow path chamber, a case that is connected to the valve body and defines an accommodation space for the rotor portion, and a speed reducing means that reduces the speed of a fluid passing through the valve port, wherein the valve body supports the valve element that is provided along the axis in the axial direction. the valve portion has a seal portion that closes the valve port and a flow path portion that can communicate with the valve port, and the rotation of the rotor changes the state of communication between the valve port and the flow path portion to control the flow rate of the fluid flowing through the valve port, and the deceleration means is an electric valve in which the valve body or the guide portion has a wall portion that directly faces the first port.

[0010] In addition, in the above-mentioned electric valve, the guide portion may be made of a guide member formed in a bottomed cylindrical shape having a bottom on the other end side, and the valve body and the outer peripheral surfaces of the guide portion may have sliding portions that are slidably engaged with each other.

[0011] In the above-described motor-operated valve, the valve body and the inner circumferential surface of the guide portion may have sliding portions that are slidably engaged with each other.

[0012] Moreover, the above-mentioned motor-operated valve may further include a rectifying means for equalizing the flow velocity distribution of the fluid passing through the valve port, and the rectifying means may be arranged so that the valve port is located on the opposite side of the axis from the first port when viewed in the axial direction.

[0013] The above-mentioned electric valve may further include a rectifying means for equalizing the flow velocity distribution of the fluid passing through the valve port, and the rectifying means may have a flow path portion that extends along the axial direction and has a flow path area that is approximately the same as the flow path area of ​​the valve port.

[0014] The above-mentioned motor-operated valve may further include a rectifying means for equalizing the flow velocity distribution of the fluid passing through the valve port, and the rectifying means may be configured to position the valve port in the guide portion on the opposite side of the wall portion with respect to the axis when viewed from the axial direction.

[0015] The present invention may also be directed to a refrigeration cycle system including a compressor, a condenser, an expansion valve, and an evaporator, in which the motor-operated valve is used as the expansion valve. [Effects of the Invention]

[0016] According to the present invention, it is possible to provide an electrically operated valve and a refrigeration cycle system using the same that are provided with a means for reducing the fluid velocity, thereby suppressing the noise of fluid passing through and improving quietness. [Brief explanation of the drawings]

[0017] [Figure 1] 1A and 1B are cross-sectional views showing an electric valve according to a first embodiment of the present invention, in which (a) is a longitudinal cross-sectional view of the electric valve, (b) is an enlarged view of the Ib-Ib cross section of (a), and (c) is an enlarged view of the area surrounded by the dashed line Ic shown in (a). [Figure 2] 2A and 2B are explanatory diagrams of the open and closed states of the motor-operated valve shown in FIG. 1, where (a) is an enlarged view of the main part in the open state, (b) is a cross-sectional view taken along line IIb-IIb shown in (a), (c) is an enlarged view of the main part in the closed state, and (d) is a cross-sectional view taken along line IId-IId shown in (c). [Figure 3] 3A and 3B are explanatory diagrams of a modified stopper portion of the first embodiment, in which (a) is a cross-sectional view corresponding to FIG. 2A, and (b) is a cross-sectional view taken along line IIIb-IIIb shown in (a). [Figure 4] 4A and 4B are cross-sectional views of a motor-operated valve according to a second embodiment of the present invention in an open state, where FIG. 4A is a longitudinal cross-sectional view of the motor-operated valve, and FIG. 4B is an enlarged cross-sectional view of FIG. 4A taken along line IVb-IVb. [Figure 5]5A and 5B are cross-sectional views of the motor-operated valve shown in FIG. 4 in a valve-closed state, where (a) is a longitudinal cross-sectional view of the motor-operated valve, and (b) is an enlarged cross-sectional view of Vb-Vb in (a). [Figure 6] FIG. 10 is an explanatory view (a cross-sectional view corresponding to FIG. 4(a)) of a modified second joint pipe of the second embodiment. [Figure 7] FIG. 10 is an explanatory view (a cross-sectional view corresponding to FIG. 4(a)) of a modified first joint pipe of the second embodiment. [Figure 8] FIG. 1 is a diagram showing a refrigeration cycle system (for cooling operation only) of the present invention. [Figure 9] 9A and 9B are cross-sectional views showing a motor-operated valve according to a conventional technique, in which (a) is a longitudinal cross-sectional view of the motor-operated valve, and (b) is an enlarged cross-sectional view taken along line IXb-IXb of (a). DETAILED DESCRIPTION OF THE INVENTION

[0018] An embodiment of the present invention will be described in detail with reference to Figures 1 to 8. However, the present invention is not limited to this embodiment.

[0019] <Terminology> In this specification and the claims, the terms "left," "right," "upper," and "lower" refer to the directions shown in Figures 1(a), 1(c), 2(a), 2(c), 3(a), 4(a), 5(a), 6, and 7. In this specification and the claims, the terms "one end" and "the other end" refer to the "lower end" and "upper end" in the drawings. In this specification and the claims, the term "speed reduction means" refers to "means for reducing the speed of a fluid passing through a valve port." In this specification and the claims, the term "flow straightening means" refers to "means for uniforming the flow velocity distribution of a fluid passing through a valve port." In this specification and the claims, the term "the flow path area of ​​the flow path portion is approximately the same as the flow path area of ​​the valve port" refers to a value that satisfies the numerical range of "1 < (flow path area of ​​the flow path portion / flow path area of ​​the valve port) ≦ 2.5."

[0020] (First embodiment) <About the configuration of the motor-operated valve> A motor-operated valve 100a according to a first embodiment of the present invention will be described using Figure 1. The motor-operated valve 100a is mainly composed of a valve body 10A, a valve element 20A, a stepping motor 30A, and a support member 40A. Each component of the motor-operated valve 100a will be described below in order.

[0021] As will be described in detail later, the motor-operated valve 100a of the first embodiment employs a speed reducing means to resolve the conventional problem (noise from the motor-operated valve) and improve quietness. Even if high-speed foreign matter flows into the motor-operated valve 100a from another fluid-connected device, the speed of the foreign matter itself can be forcibly reduced, thereby preventing damage to the seal portion 20aa, the valve port 11a, etc. Additionally, the motor-operated valve 100a of the first embodiment employs a flow straightening means to resolve the concern (uneven flow velocity distribution), further reduce the noise of fluid passage, and further improve quietness.

[0022] The valve body 10A comprises a bowl-shaped member 10 that defines a portion of the flow path chamber 13, and a guide member 11 that has an approximately cylindrical shape extending along the axis L and is fixedly connected to the bottom side of the bowl-shaped member 10.

[0023] A first coupling pipe 1 and a second coupling pipe 2, which serve as fluid paths for a refrigerant or the like, are connected to the bottom side of the bowl-shaped member 10. The first coupling pipe 1 is directly connected to a flow path chamber 13 via a first port 1a. The second coupling pipe 2 is abutted against one end of a guide member 11 and is connected to the flow path chamber 13 via the second port 2a, an internal flow path 14 of the guide member 11, and a valve port 11a (described in detail below). The first coupling pipe 1 and the second coupling pipe 2 are made of materials such as copper or stainless steel, and are fixed to the bowl-shaped member 10 by brazing or the like. As shown in FIG. 1(b), the bowl-shaped member 10 is formed with a raised portion 10a that is located on the opposite side of the first coupling pipe 1 with respect to the axis L when viewed from the direction of the axis L and that raises toward the flow path chamber 13.

[0024] The guide member 11 has a significantly different structure from approximately the center in the axial direction L to one end side and the other end side. First, the guide member 11 from approximately the center in the axial direction L to one end side has a cylindrical shape with a bottom. It has an internal flow path 14 extending in the axial direction L. As shown in FIG. 1(c), at the other end side of the internal flow path 14, it has a valve port 11a that radially penetrates the guide member 11 and an annular valve seat 11b formed around the valve port 11a. Next, the guide member 11 from approximately the center in the axial direction L to the other end side has a solid shape, and a flat support portion 11e is formed at the other end of the guide member 11. Here, the valve port 11a is located on the opposite side of the axial direction L from the first port 1a, as shown in FIGS. 2(b) and 2(d). In the first embodiment, the shape of the valve port 11a when viewed from a direction perpendicular to the axis L is circular, but this is not limited to this and various shapes can be adopted, such as a rectangular shape, an elliptical shape, or any asymmetric shape.

[0025] In the first embodiment, the bowl-shaped member 10 and the guide member 11 are separate bodies, but this is not limiting. For example, the bowl-shaped member 10 and the guide member 11 may be integrally formed as in the conventional motor-operated valve shown in FIG. 9(a).

[0026] The valve disc 20A is a member extending along the axis L. The valve disc 20A has a valve portion 20a formed at one end. The inside of the valve disc 20A includes a first-end, bottomed cylindrical portion 20b extending toward one end along the axis L and an opposite-end, bottomed cylindrical portion 20c extending toward the other end along the axis L. The valve disc 20A is provided, on its outer periphery, with a flange portion 20g protruding in a disk shape from the radially outer side of the valve portion 20a, and a protrusion 20e extending downward from the flange portion 20g and protruding from the radially outer side of the valve portion 20a to come into contact with the raised portion 10a of the bowl-shaped member 10 when the valve disc 20A rotates. As shown in FIG. 1(b), the flange portion 20g is positioned so as to overlap the first port 1a when viewed from the direction of the axis L. Therefore, the flange portion 20g functions as a deceleration means, as will be described in detail below. The valve body 20A is provided on its outer periphery with a step 20d into which the magnet rotor 32 is fitted and abuts, and an annular groove 20f that holds the retaining ring 17, as will be described in detail later.

[0027] The guide member 11, which guides the valve element 20A in the circumferential direction, is inserted into the bottomed cylindrical portion 20b with a small radial gap to allow sliding movement. The outer peripheral surfaces of the bottomed cylindrical portion 20b and the guide portion 11d have sliding portions that slidably engage with each other. This enhances the stability of the rotational state of the valve element 20A. The other end 20ba of the bottomed cylindrical portion 20b, which abuts against the support portion 11e of the guide member 11, has a flat shape corresponding to the support portion 11e. The bottomed cylindrical portion 20b, as will be described in detail later, has a seal portion 20aa that annularly slides against the valve seat 11b of the guide member 11, and a flow path portion 15 that has a shape that combines a substantially fan-shaped shape with a semicircular shape eccentric to the axis L when viewed from the axis L, and that opens to one end of the bottomed cylindrical portion 20b in the axis L direction. 2(a), one end 15a of this flow path portion 15 is disposed on one end side of the valve port 11a in the direction of the axis L, and the other end 15b of the flow path portion 15 is disposed on the other end side of the valve port 11a in the direction of the axis L. In the first embodiment, the shape of the support portion 11e of the guide member 11 is flat, but this is not limiting and it may be, for example, hemispherical or convex. This significantly reduces the contact area between the support portion 11e of the guide member 11 and the other end 20ba of the valve element 20A, reducing sliding resistance and making it easier for the valve element 20A to rotate.

[0028] The other end side bottomed cylindrical portion 20c accommodates a support member 40A that biases the valve body 20A toward one end side.

[0029] Therefore, when the valve portion 20a rotates relative to the guide member 11, the communication state between the flow path portion 15 of the valve portion 20a and the valve port 11a of the guide member 11 is changed between a valve open state (see FIGS. 2(a) and 2(b)) and a valve closed state (see FIGS. 2(c) and 2(d)) (or a minimum opening), thereby adjusting the flow rate. At this time, as shown in FIGS. 2(b) and 2(d), the protrusion 20e of the valve portion 20a abuts against the raised portion 10a, which functions as a stopper, thereby restricting the rotation of the valve portion 20a and the rotation of the magnet rotor 32. Therefore, the valve portion 20a is restricted from moving beyond the position where the valve is open or the position where the valve is closed (or a minimum opening), allowing for stable and reliable positioning with reproducibility.

[0030] The stepping motor 30A includes a case 31, a magnet rotor 32, and a stator coil 33.

[0031] The case 31 is made of a metal such as stainless steel and is formed in a generally cylindrical shape with a closed upper end, defining an accommodation space 16 that accommodates the valve body 20A and the magnet rotor 32. The lower open end of the case 31 is airtightly fixed to the upper end of the bowl-shaped member 10 by welding or the like.

[0032] The magnet rotor 32 integrally comprises a cylindrical magnet section 34 whose outer periphery is magnetized with multiple poles, and a hub 35 connected via spokes to the inner periphery of the magnet section 34. The magnet rotor 32 is fixed to the valve body 20A by abutting one end of the hub 35 against the step portion 20d and clamping the other end of the hub 35 with a retaining ring 17 so as to be biased in the direction of the axis L. In this way, the rotor section integrally has the magnet rotor 32 and the valve body 20A and is provided within the case 31 so as to be rotatable about the axis L.

[0033] The stator coil 33 is disposed on the outer peripheral surface of the case 31, and when a pulse signal is given to the stator coil 33, the magnet rotor 32 is rotated in accordance with the number of pulses.

[0034] In this way, when the magnet rotor 32 rotates, the valve portion 20a rotates together with the magnet rotor 32 relative to the valve port 11a, changing the opening degree between the flow path portion 15 and the valve port 11a, and controlling the flow rate of the fluid flowing from the first joint pipe 1 to the second joint pipe 2, as will be described in detail later.

[0035] The support member 40A includes a spring receiving portion 41 that is rotatably arranged in contact with the case 31, and a biasing spring 42 that is sandwiched between the spring receiving portion 41 and the valve body 20A and biases the valve body 20A toward one end.

[0036] <Operation of the motor-operated valve> The operation of the motor-operated valve 100a will be described using Figure 2. Here, the motor-operated valve 100a will be described as being used in a refrigerant circuit, but is not limited to this. In the motor-operated valve 100a, the first joint pipe 1 is connected to the high-pressure (primary pressure) side, and the second joint pipe 2 is connected to the low-pressure (secondary pressure) side.

[0037] First, as shown in FIG. 2(b), the valve portion 20a is rotated counterclockwise (in the direction of the arrow) by the magnet rotor 32, causing the protrusion 20e of the valve portion 20a to abut against the raised portion 10a of the bowl-shaped member 10, restricting the rotation of the valve portion 20a and the magnet rotor 32. At this time, the flow path portion 15 faces the valve port 11a, resulting in an open valve state. Therefore, fluid flows from the first port 1a on the high-pressure side to the second port 2a on the low-pressure side, as indicated by the solid arrow in FIG. 2(a). To prevent pressure loss in the fluid path, the flow path area of ​​the flow path portion 15 and the internal flow path 14, located before and after the valve port 11a, are set to be larger than the flow path area of ​​the valve port 11a. The flow path area of ​​the flow path section 15 is approximately the same as the flow path area of ​​the valve port 11a, and satisfies the numerical range of 1<(flow path area of ​​the flow path section 15 / flow path area of ​​the valve port 11a)≦2.5.

[0038] 2(d), the valve portion 20a is rotated clockwise (in the direction of the arrow) by the magnet rotor 32, causing the protrusion 20e of the valve portion 20a to abut against the raised portion 10a of the bowl-shaped member 10, restricting the rotation of the valve portion 20a and also restricting the rotation of the magnet rotor 32. At this time, the flow path portion 15 faces the valve seat 11b, and the valve port 11a faces the seal portion 20aa, resulting in a valve-closed state. This closes the flow path from the first port 1a on the high-pressure side to the second port 2a on the low-pressure side.

[0039] The flow path section 15 in the first embodiment has a shape that combines a substantially fan-shaped shape and a semicircular shape that is eccentric with respect to the axis L when viewed in the direction of the axis L. Therefore, in the first embodiment, when the flow path section 15 rotates with respect to the valve port 11a and transitions from one of the valve open state (see FIG. 2(b)) and the valve closed state (see FIG. 2(d)) to the other, the flow path area decreases abruptly immediately after the transition and then gradually decreases, or the flow path area changes gradually and then rapidly increases. In this way, the motor-operated valve 100a in the first embodiment is capable of flow rate control by a combination of abrupt and gradual changes in the flow path area, and therefore can be used, for example, as an on-off valve that has the added function of a flow rate adjustment valve.

[0040] Although the flow path section 15 in the first embodiment has a shape that combines a substantially fan-shaped shape as viewed from the direction of the axis L and a semicircular shape that is eccentric with respect to the axis L, the shape is not limited thereto. For example, when the flow path section 15 in the first embodiment has a substantially fan-shaped shape as viewed from the direction of the axis L, in the motor-operated valve 100a, the flow path section 15 rotates relative to the valve port 11a, and when the motor-operated valve 100a transitions from one of the valve-open state and the valve-closed state to the other, the flow path area rapidly decreases or increases immediately after the transition, and therefore the motor-operated valve 100a can be used, for example, as an on-off valve. Furthermore, when the flow path section 15 in the first embodiment has a semicircular shape that is eccentric with respect to the axis L as viewed from the direction of the axis L, the flow path section 15 rotates relative to the valve port 11a, and when the motor-operated valve 100a transitions from one of the valve-open state and the valve-closed state to the other, the flow path area gradually decreases or increases, enabling fine flow rate control, and therefore the motor-operated valve 100a can be used, for example, as a flow rate adjustment valve.

[0041] <About deceleration methods> In the motor-operated valve 100a of the first embodiment, in the valve open state, a high-speed fluid flows in through the first port 1a, as in conventional motor-operated valves. If no countermeasures are taken, the high-speed fluid flows directly into the valve port 11a, generating a fluid passage noise and potentially resulting in the conventional problem (noise from the motor-operated valve). Therefore, in the first embodiment, in order to suppress the fluid passage noise, a deceleration means (impingement against a wall surface) is employed for the high-speed fluid flowing in through the first port 1a. The deceleration means (impingement against a wall surface) in the first embodiment will be described below with reference to FIGS. 2(a) and 2(b). The fluid path (solid line) in FIG. 2(a) and the impingement point Ip in FIGS. 2(a) and 2(b) are exaggerated to facilitate understanding.

[0042] <About deceleration methods (collision with wall surface)> The deceleration means (impinging on the wall surface) in the first embodiment will be described using Figures 2(a) and (b). In the valve open state, fluid flows from the first port 1a through the flow path chamber 13, the flow path section 15, the valve port 11a, and the internal flow path 14, in this order, to the second port 2a, as shown by the solid arrow in Figure 2(a). Here, the deceleration means (impinging on the wall surface) causes the high-speed fluid flowing from the first port 1a into the flow path chamber 13 to collide with the flange one end face 20ga (wall surface) directly opposite the first port 1a, forcibly slowing down the fluid. As a result, the fluid passing through the valve port 11a is in a decelerated flow state, which solves the conventional problem (noise from the motor-operated valve), i.e., suppresses the sound of the fluid passing through, improving quietness.

[0043] <Regarding rectification means> At the collision point Ip where the fluid collides, the high-speed fluid is forcibly decelerated, while multiple three-dimensional vortices are generated around the collision point Ip. If these three-dimensional vortices have a locally high flow velocity and flow directly into the valve port 11a without being attenuated, there is a risk that fluid passing noise will be generated due to uneven flow velocity distribution (hereinafter referred to as "concern (uneven flow velocity distribution)"). For this reason, in the first embodiment, by further employing a first rectifying means (long fluid path) and a second rectifying means (narrow flow path), the concern (uneven flow velocity distribution) can be resolved, fluid passing noise can be further suppressed, and quietness can be further improved.

[0044] <Regarding the first flow straightening means (long fluid path)> As shown in FIG. 2(a), the first rectifying means (long fluid path) lengthens the fluid path from the collision point Ip to the valve port 11a. The viscous resistance of the fluid along this long fluid path damps the generated three-dimensional vortices and homogenizes the flow velocity distribution. Specifically, because the valve port 11a is located on the opposite side of the axis L from the first port 1a, the fluid flows from the collision point Ip along the outer periphery of the valve portion outer wall 20ab, flows toward the one end by the protrusion 20e, and then flows toward the valve port 11a by the bottom surface of the flow path chamber 13. Because the flow velocity at the one end 15a of the flow path 15 is reduced, even if wear debris or foreign matter (hereinafter referred to as "wear debris") accumulates on the bottom surface of the flow path chamber 13, the wear debris will not be stirred up and mixed into the fluid path.

[0045] <Regarding the second flow straightening means (narrow flow path portion)> 2(a), the second rectifying means (narrow flow path portion) passes the damped three-dimensional vortex through a flow path portion 15 that is much smaller than the flow path chamber 13 and has a flow path area approximately the same as the valve port 11a, and this narrow flow path portion 15 acts like a flow straightening grid, forcibly dividing the damped three-dimensional vortex, thereby eliminating the three-dimensional vortex. Furthermore, the second rectifying means (narrow flow path portion) has a turbulent boundary layer with abrupt velocity changes near the wall surface of the flow path portion 15, resulting in a trapezoidal velocity distribution, which makes it possible to homogenize the flow velocity distribution compared to laminar Hagen-Poiseuille flow, which has a parabolic velocity distribution.

[0046] As described above, the motor-operated valve 100a in the first embodiment employs a deceleration means (impingement on a wall surface), and by forcibly decelerating the high-speed fluid flowing from the first port 1a into the flow path chamber 13 by impinging it on the flange portion one end face 20ga (wall surface) directly opposite the first port 1a, the conventional problem (noise from the motor-operated valve) can be resolved, that is, the noise of the fluid passing through can be suppressed and quietness can be improved. Furthermore, even if a high-speed foreign object flows into the motor-operated valve 100a from another fluid-connected device, the speed of the foreign object itself can be forcibly decelerated, thereby suppressing damage to the seal portion 20aa, the valve port 11a, etc.

[0047] Additionally, the motor-operated valve 100a in the first embodiment employs first and second rectification means (a long fluid path and a narrow flow path section). In this manner, in the first embodiment, the fluid path from the collision point Ip to the valve port 11a is lengthened, thereby attenuating multiple three-dimensional vortices generated around the collision point Ip due to the viscous resistance of the fluid. Furthermore, the attenuated three-dimensional vortices pass through the flow path section 15, which has a relatively small flow path area, forcibly eliminating the three-dimensional vortices and uniforming the flow velocity distribution. As a result, the motor-operated valve 100a in the first embodiment resolves the concern (uneven flow velocity distribution), further suppresses the fluid passing noise at the valve port 11a, and further improves quietness.

[0048] (Modification of the stopper portion of the first embodiment) A modified stopper portion of the first embodiment will be described using Figure 3. The connection mode of the first joint pipe 1' in the modified stopper portion of the first embodiment differs from that of the first embodiment in that the first joint pipe 1' extending in a direction perpendicular to the axis L is disposed at a position where it functions as a stopper portion for the valve portion 20a, and the raised portion 10a is omitted. However, the other configurations are the same as those of the first embodiment. Here, the same configurations are denoted by the same reference numerals, and duplicated explanations will be omitted.

[0049] Specifically, in the bowl-shaped member 10', the first coupling pipe 1' is positioned so that it overlaps with the protrusion 20e when viewed from a direction perpendicular to the axis L, as shown in FIG. 3(a), and is positioned so that it interferes with the rotating protrusion 20e when viewed from the direction of the axis L, as shown in FIG. 3(b). When the first coupling pipe 1' abuts against the rotating protrusion 20e, the rotation angle is restricted to a desired angle, allowing for stable, reliable positioning with reproducibility. In this way, the first coupling pipe 1' functions as a stopper for the valve portion 20a, so the protrusion 10a can be omitted, resulting in cost reduction.

[0050] <About deceleration methods> The motor-operated valve 100b in the modified stopper portion of the first embodiment employs a deceleration means (impingement on a wall surface) to suppress fluid passage noise in the valve port 11a, as in the first embodiment. This decelerates the fluid passing through the valve port 11a, thereby suppressing fluid passage noise and improving quietness. The deceleration means (impingement on a wall surface) in the modified stopper portion of the first embodiment will be described below. Note that the fluid path (solid line) in FIG. 3(a) and the collision portion Ip in FIGS. 3(a) and 3(b) are exaggerated to facilitate understanding of the description.

[0051] <About deceleration methods (collision with wall surface)> 3(a) and (b), the deceleration means (impinging on the wall surface) in the modified stopper portion of the first embodiment will be described. In the valve open state, fluid flows from the first port 1a' through the flow path chamber 13, the flow path portion 15, the valve port 11a, and the internal flow path 14, in this order, to the second port 2a, as indicated by the solid arrow in FIG. 3(a). The deceleration means (impinging on the wall surface) causes the high-speed fluid flowing from the first port 1a' into the flow path chamber 13 to collide with the valve portion outer peripheral wall 20ab and the protrusion 20e (wall surface) directly opposite the first port 1a', forcibly slowing down the fluid. This decelerates the fluid flowing through the valve port 11a, thereby eliminating the conventional problem (noise from the motor-operated valve). In other words, it is possible to suppress the sound of the fluid passing through the valve port 11a and improve quietness.

[0052] <Regarding rectification means> At the collision point Ip where the fluid collides, the high-speed fluid is forcibly decelerated, and multiple three-dimensional vortices are generated, particularly around the protrusion 20e. If these three-dimensional vortices have a locally high flow velocity and flow directly into the valve port 11a without being attenuated, there is a risk of a concern (uneven flow velocity distribution). For this reason, in the stopper portion modification of the first embodiment, by further employing a second rectifying means (narrow flow path portion) as in the first embodiment, the concern (uneven flow velocity distribution) is resolved, the flow velocity distribution of the fluid passing through the valve port 11a is made uniform, and the fluid passing noise is further suppressed, resulting in further improvement in quietness.

[0053] <Regarding the second flow straightening means (narrow flow path portion)> 3(a), the second rectifying means (narrow flow path portion) causes the generated three-dimensional vortex to pass through a flow path portion 15 that is much smaller than the flow path chamber 13 and has a flow path area approximately the same as the valve port 11a, and this narrow flow path portion 15 acts like a flow straightening grid, forcibly breaking up the attenuated three-dimensional vortex, thereby eliminating the three-dimensional vortex. Furthermore, the second rectifying means (narrow flow path portion) has a turbulent boundary layer with abrupt velocity changes near the wall surface of the flow path portion 15, resulting in a trapezoidal velocity distribution, which makes it possible to homogenize the flow velocity distribution compared to laminar Hagen-Poiseuille flow, which has a parabolic velocity distribution.

[0054] As described above, the motor-operated valve 100b in the stopper portion modification of the first embodiment employs a deceleration means (impingement on a wall surface), and similarly to the first embodiment, the high-speed fluid flowing from the first port 1a into the flow path chamber 13 is forcibly decelerated by impinging on the valve portion outer peripheral wall 20ab (wall surface) directly opposite the first port 1a, thereby eliminating the conventional problem (noise from the motor-operated valve), that is, suppressing the sound of the fluid passing through and improving quietness. Furthermore, even if a high-speed foreign object flows into the motor-operated valve 100b from another fluid-connected device, the speed of the foreign object itself can be forcibly decelerated, thereby suppressing damage to the seal portion 20aa, the valve port 11a, etc.

[0055] In addition, the motor-operated valve 100b in the modified stopper portion of the first embodiment employs a second rectifying means (narrow flow path portion), and similarly to the first embodiment, by passing the fluid through the flow path portion 15 having a relatively small flow path area, it is possible to forcibly eliminate three-dimensional vortices and make the flow velocity distribution uniform. As a result, the motor-operated valve 100a in the first embodiment can eliminate the concern (uneven flow velocity distribution), further suppress the fluid passing noise in the valve port 11a, and further improve quietness.

[0056] (Second embodiment) A motor-operated valve 100c according to a second embodiment will be described using Figure 4. The motor-operated valve 100c according to the second embodiment differs from the motor-operated valve 100a according to the first embodiment mainly in the radial arrangement of the valve body 20B and the guide portions 11Bca, 11Bcb, and the connection mode of the first joint pipe 1B and the second joint pipe 2B, but the other basic configuration is substantially the same as that of the first embodiment. Here, the same configuration is given the same reference numeral, and duplicated explanations will be omitted.

[0057] <About the configuration of the motor-operated valve> 4, the motor-operated valve 100c is mainly composed of a valve body 10B, a valve element 20B, a stepping motor 30B, and a support member 40B. Each component of the motor-operated valve 100c will be described below in order.

[0058] As will be described in detail later, the motor-operated valve 100c of the second embodiment, like the first embodiment, employs a deceleration means (impact on a wall surface) to resolve the conventional problem (noise from the motor-operated valve) and improve quietness. Even if high-speed foreign matter flows into the motor-operated valve 100c from another fluid-connected device, the speed of the foreign matter itself can be forcibly reduced, thereby preventing damage to the seal portion 20Baa (see FIG. 5(b)) or the valve port 11Ba. Additionally, the motor-operated valve 100c of the second embodiment employs a third flow straightening means (positioning the valve port at a downstream stagnation point) to resolve the concern (uneven flow velocity distribution), further suppress fluid passage noise, and further improve quietness.

[0059] The valve body 10B comprises a bowl-shaped member 10Ba that defines a portion of the flow path chamber 13, a guide member 11B that has an approximately cylindrical shape extending along the axis L and is fixedly connected to the bottom side of the bowl-shaped member 10Ba, and a lower cover 12 that is annular and integrally molded with the guide member 11B.

[0060] A first joint pipe 1B, which serves as a fluid path for a refrigerant or the like, is connected to the side surface of the bowl-shaped member 10Ba, and a second joint pipe 2B, which serves as a fluid path for a refrigerant or the like, is connected to the bottom surface of the bowl-shaped member 10Ba. The first joint pipe 1B is directly connected to the flow path chamber 13 via the first port 1Ba. The second joint pipe 2B is connected to the flow path chamber 13 via the second port 2Ba, an internal flow path 14 of the guide member 11B, and a valve port 11Ba (details will be described later). The first joint pipe 1B and the second joint pipe 2B are made of a material such as copper or stainless steel, and are fixed to the bowl-shaped member 10Ba by brazing or the like.

[0061] An insertion hole that opens from one end to the other end along the axis L is formed in the guide member 11B. A large-diameter guide portion 11Bcb and a small-diameter guide portion 11Bca are provided in this insertion hole from the other end to the one end. The small-diameter guide portion 11Bca has an inner diameter smaller than that of the large-diameter guide portion 11Bcb, and an internal flow path 14 extending in the direction of the axis L is defined in the inner region on the one end side. In addition, a flat, annular support portion 11Be is formed at the boundary between the large-diameter guide portion 11Bcb and the small-diameter guide portion 11Bca. 4(a), the guide member 11B is formed with a valve port 11Ba that is located concentrically with the first port 1Ba and on the opposite side of the axis L from the first joint pipe 1B with respect to the axis L, and that penetrates radially between the internal flow path 14 and the flow path chamber 13, and an annular valve seat 11Bb (see FIG. 4(b)) that is formed around the valve port 11Ba. In addition, a drawn-out portion 11Bg that extends radially outward is formed on part of the outer circumferential surface on the other end side of the guide member 11B.

[0062] The lower cover 12 has an inner peripheral portion joined to the guide member 11B, and an outer peripheral portion joined to the other end of the bowl-shaped member 10Ba and one end of the case 31B.

[0063] In the second embodiment, the shape of the valve port 11Ba when viewed from a direction perpendicular to the axis L is circular, but this is not limited to this and various shapes can be used, such as a rectangular shape, an elliptical shape, or any asymmetric shape. Also, in the second embodiment, the bowl-shaped member 10Ba and the guide member 11B are separate bodies, but this is not limited to this and, for example, the bowl-shaped member 10Ba and the guide member 11B may be formed integrally as in the conventional motor-operated valve shown in Figure 9(a).

[0064] The valve element 20B is a member extending along the axis L. One end of the valve element 20B is inserted into an insertion hole in the guide member 11B, and from one end to the other, a valve portion 20Ba, a small-diameter guide shaft portion 20Bg, and a large-diameter guide shaft portion 20Bh are formed, each of which increases in diameter in a stepped manner. A flat, annular one-end step portion 20Bi is formed at the boundary between the small-diameter guide shaft portion 20Bg and the large-diameter guide shaft portion 20Bh. As shown in FIG. 4(b), the valve portion 20Ba has a semicircular shape eccentric with respect to the axis L when viewed from the direction of the axis L, and includes a flow path portion 15B that opens at one end in the direction of the axis L. The small-diameter guide shaft portion 20Bg, the one-end step portion 20Bi, and the large-diameter guide shaft portion 20Bh each have a sliding portion that slidably engages with the small-diameter guide portion 11Bca, the support portion 11Be, and the large-diameter guide portion 11Bcb of the guide member 11B, respectively. This allows the valve body 20B of the second embodiment to be relatively smaller in radial size and lighter in weight than the valve body 20A of the first embodiment, thereby improving energy efficiency of the stepping motor 30B. The other end of the valve body 20B further includes a other-end step portion 20Bka that is fixed to the hub 35B of the magnet rotor 32B, and a other-end bottomed cylindrical portion 20Bc that extends along the axis L to the other end and opens. The other-end bottomed cylindrical portion 20Bc accommodates a support member 40B that biases the valve body 20B toward the one end.

[0065] Therefore, as the valve portion 20Ba rotates relative to the small-diameter guide portion 11Bca, the communication state between the flow path portion 15B of the valve portion 20Ba and the valve port 11Ba of the small-diameter guide portion 11Bca changes between a valve open state (see FIGS. 4(a) and 4(b)) and a valve closed state (see FIGS. 5(a) and 5(b)) (or a minimum opening), thereby adjusting the flow rate. At this time, as will be described in detail later, as shown in FIG. 5(a), the protrusion 20Bkb extending downward from the disk portion 20Bk of the valve element 20B abuts against the drawn-out portion 11Bg of the guide member 11B, which functions as a stopper, thereby restricting the rotation of the valve portion 20Ba and the magnet rotor 32B. Therefore, the valve portion 20Ba is restricted from moving beyond the position where the valve is open or the position where the valve is closed (or a minimum opening), allowing for stable, reliable positioning with reproducibility.

[0066] The stepping motor 30B includes a case 31B, a magnet rotor 32B, and a stator coil 33B. Note that the stator coil 33B is the same as that in the first embodiment, and therefore a description thereof will be omitted.

[0067] The case 31B is made of a metal such as stainless steel and is formed in a generally cylindrical shape with a closed upper end, defining an accommodation space 16 that accommodates the valve body 20B and the magnet rotor 32B. The lower open end of the case 31B is airtightly fixed to the outer periphery of the bottom cover 12 by welding or the like.

[0068] The magnet rotor 32B integrally includes a cylindrical magnet portion 34B and a cylindrical hub 35B connected to the inner periphery of the magnet portion 34B. The valve element 20B is inserted into the inside of the hub 35B of the magnet rotor 32B toward the other end in the direction of the axis L. The other-end step 20Bka of the valve element 20B is brought into contact with one end of the hub 35B. A bushing 43 of a support member 40B (described below) is incorporated into the other-end bottomed cylindrical portion 20Bc and brought into contact with the other end of the hub 35B. After that, the magnet rotor 32B, which serves as the rotor portion, and the valve element 20B are integrally fixed to the hub 35B by welding or the like. This allows the rotor portion to be rotatable about the axis L within the case 31B.

[0069] In this way, when the magnet rotor 32B rotates, the valve portion 20Ba rotates together with the magnet rotor 32B relative to the valve port 11Ba, changing the opening degree between the flow path portion 15B and the valve port 11Ba, and controlling the flow rate of the fluid flowing from the first joint pipe 1B to the second joint pipe 2B, as will be described in detail later.

[0070] The support member 40B includes a spring receiving portion 41 that is rotatably arranged in contact with the case 31B, a bushing 43 that is fixed to the bottomed cylindrical portion 20Bc on the other end side and the hub 35B, and a biasing spring 42 that is sandwiched between the spring receiving portion 41 and the bushing 43 and biases the valve body 20B toward one end.

[0071] <Operation of the motor-operated valve> The operation of the motor-operated valve 100c will be described using Figures 4 and 5. Here, the motor-operated valve 100c will be described as being used in a refrigerant circuit, but is not limited to this. In the motor-operated valve 100c, the first joint pipe 1B is connected to the high-pressure (primary pressure) side, and the second joint pipe 2B is connected to the low-pressure (secondary pressure) side.

[0072] First, as shown in FIG. 4(b), the valve portion 20Ba is rotated counterclockwise by the magnet rotor 32B. As a result, the protrusion 20Bkb of the valve element 20B abuts against the drawn-out portion 11Bg of the guide member 11B (not shown), restricting the rotation of the valve portion 20Ba and the magnet rotor 32B. At this time, the flow path portion 15B faces the valve port 11Ba, resulting in an open valve state. Therefore, fluid flows from the first port 1Ba on the high-pressure side to the second port 2Ba on the low-pressure side, as indicated by the solid arrows in FIGS. 4(a) and 4(b). To prevent pressure loss in the fluid path, the flow path areas of the flow path chamber 13 and the flow path portion 15B, located before and after the valve port 11Ba, are set larger than the flow path area of ​​the valve port 11Ba.

[0073] Next, as shown in FIG. 5(b), the valve portion 20Ba is rotated clockwise by the magnet rotor 32B, and as shown in FIG. 5(a), the protrusion 20Bkb of the valve element 20B abuts against the drawn-out portion 11Bg of the guide member 11B, restricting the rotation of the valve portion 20Ba and also restricting the rotation of the magnet rotor 32B. At this time, the flow path portion 15B faces the valve seat 11Bb, and the valve port 11Ba faces the seal portion 20Baa, resulting in a valve-closed state. Therefore, the flow path from the first port 1Ba on the high-pressure side to the second port 2Ba on the low-pressure side is closed.

[0074] The flow path portion 15B in the second embodiment has a semicircular shape that is eccentric with respect to the axis L when viewed in the direction of the axis L. Therefore, in the motor-operated valve 100c in the second embodiment, when the flow path portion 15B rotates with respect to the valve port 11Ba and transitions from one of the valve open state and the valve closed state to the other, the flow path area gradually decreases or increases, enabling fine flow rate control, and therefore the motor-operated valve can be used, for example, as a flow rate adjustment valve.

[0075] Although the flow path portion 15B in the second embodiment has a semicircular shape that is eccentric with respect to the axis L when viewed in the direction of the axis L, this is not limited to this. For example, if the flow path portion 15B in the second embodiment has a substantially fan shape when viewed in the direction of the axis L, in the motor-operated valve 100c, when the flow path portion 15B rotates with respect to the valve port 11Ba and transitions from one of the valve open state and the valve closed state to the other, the flow path area rapidly decreases or increases immediately after the transition, and therefore the motor-operated valve can be used, for example, as an on-off valve. Furthermore, in the second embodiment, when the flow path section 15B has a shape that combines an approximately fan-shaped shape and a semicircular shape that is eccentric with respect to the axis L when viewed from the direction of the axis L, in the electric valve 100c, when the flow path section 15B rotates relative to the valve port 11Ba and transitions from one of the valve open state and the valve closed state to the other, the flow path area decreases abruptly immediately after the transition and then the flow path area changes gradually, or the flow path area changes gradually and then the flow path area increases abruptly, and therefore the electric valve 100c can be used, for example, as an opening / closing valve with the added function of a flow control valve.

[0076] <About deceleration methods> The motor-operated valve 100c of the second embodiment employs a deceleration means (impingement on a wall surface) to suppress fluid passage noise in the valve port 11Ba, as in the first embodiment. This causes the fluid passing through the valve port 11Ba to enter a decelerated flow state, thereby suppressing fluid passage noise and improving quietness. The deceleration means (impingement on a wall surface) of the second embodiment will be described below. Note that the fluid path (solid lines) and the collision portion Ip in Figures 4(a) and (b) are exaggerated to facilitate understanding of the description.

[0077] <About deceleration methods (collision with wall surface)> The deceleration means (impinging on the wall surface portion) in the second embodiment will be described with reference to Figures 4(a) and (b). In the valve open state, as shown by the solid arrow in Figure 4(a), the fluid flows from the first port 1Ba through the flow path chamber 13, the valve port 11Ba, the flow path portion 15, and the internal flow path 14, in that order, to the second port 2Ba. Here, the deceleration means (impinging on the wall surface portion) causes the high-speed fluid flowing from the first port 1Ba into the flow path chamber 13 to collide with the guide member outer peripheral wall 11Bf (wall surface portion) directly opposite the first port 1Ba, forcibly slowing down the fluid. As a result, the fluid passing through the valve port 11Ba flows at a reduced speed, which solves the conventional problem (noise from the motor-operated valve). In other words, the fluid passing noise is suppressed, improving quietness.

[0078] <Regarding rectification means> At the collision point Ip (the so-called upstream stagnation point) where the fluids collide, the high-speed fluid is forcibly decelerated, while two-dimensional longitudinal vortices consisting of Karman vortices are alternately generated downstream. These two-dimensional longitudinal vortices have locally high flow velocities, and if they flow directly into the valve port 11Ba without being attenuated, there is a risk of causing a concern (uneven flow velocity distribution). For this reason, in the second embodiment, by further employing a third rectification means (locating the valve port at the downstream stagnation point), the concern (uneven flow velocity distribution) can be resolved, the fluid passing noise can be further suppressed, and quietness can be further improved.

[0079] <Third flow straightening method (placing the valve port at the downstream stagnation point)> The third rectification means (locating the valve port at the downstream stagnation point) is to locate the valve port 11Ba at the downstream stagnation point in the guide member 11B, as shown in FIG. 4(b). This location of the valve port 11Ba prevents the flow to the valve port 11Ba from being affected by two-dimensional longitudinal vortices and homogenizes the flow velocity distribution. Specifically, when viewed from the direction of the axis L, a high-speed fluid from the first port 1Ba collides with the guide member outer peripheral wall 11Bf (wall surface portion), forming a downstream stagnation point on the guide member outer peripheral wall 11Bf on the opposite side of the axis L from the collision point Ip (upstream stagnation point). Here, the two-dimensional longitudinal vortices that drop off from the guide member outer peripheral wall 11Bf drop off from a separation point on the collision point Ip side of the valve port 11Ba. Therefore, by providing the valve port 11Ba at the downstream stagnation point, the flow to the valve port 11Ba is not affected by two-dimensional longitudinal vortices, and the flow velocity distribution can be made uniform by the retention at the downstream stagnation point.

[0080] As described above, the motor-operated valve 100c in the second embodiment employs a deceleration means (impingement on a wall surface), and similarly to the first embodiment, the high-speed fluid flowing from the first port 1Ba into the flow path chamber 13 is forcibly decelerated by impinging on the guide member outer peripheral wall 11Bf (wall surface) directly opposite the first port 1Ba, thereby eliminating the conventional problem (noise from the motor-operated valve), that is, suppressing the sound of the fluid passing through and improving quietness. Furthermore, even if a high-speed foreign object flows into the motor-operated valve 100c from another fluid-connected device, the speed of the foreign object itself can be forcibly decelerated, thereby suppressing damage to the seal portion 20Baa, the valve port 11Ba, etc.

[0081] In addition, the motor-operated valve 100c in the second embodiment employs a third flow straightening means (locating the valve port at the downstream stagnation point), and because the valve port 11Ba is located at the downstream stagnation point, it is not affected by two-dimensional longitudinal vortices and can uniformize the flow velocity distribution. As a result, the motor-operated valve 100c in the second embodiment eliminates the concern (uneven flow velocity distribution), further suppresses the fluid passing noise at the valve port 11Ba, and further improves quietness.

[0082] (Modification of the second joint pipe of the second embodiment) A modified second joint pipe of the second embodiment will be described using Figure 6. The connection mode of the second joint pipe 2B' in the modified second joint pipe of the second embodiment differs from that of the second embodiment in that the second joint pipe 2B' is arranged so as to extend in a direction perpendicular to the axis L relative to the valve body 10B', but the other configurations are the same as those of the second embodiment. Here, the same configurations are given the same symbols, and duplicated explanations will be omitted.

[0083] Specifically, a connection chamber 18 into which the guide member 11B is fitted and fixed is formed on the bottom side of the bowl-shaped member 10Ba'. The second joint pipe 2B' is connected radially from this connection chamber 18. In this way, in the motor-operated valve 100d, by arranging the second joint pipe 2B' to extend in a direction perpendicular to the axis L, it is possible to reduce the height in the direction of the axis L.

[0084] <Regarding the speed reduction means and rectification means> The motor-operated valve 100d in the second joint pipe modification of the second embodiment employs a deceleration means (impingement on a wall surface) to suppress fluid passage noise at the valve port 11Ba, as in the second embodiment. This decelerates the fluid passing through the valve port 11Ba, thereby suppressing fluid passage noise and improving quietness. Similarly to the second embodiment, the motor-operated valve 100d in the second joint pipe modification of the second embodiment also employs a third flow rectification means (positioning the valve port at a downstream stagnation point) to homogenize the flow velocity distribution of the fluid passing through the valve port 11Ba, further suppressing fluid passage noise and further improving quietness. Note that the fluid path (solid lines) and the collision point Ip in FIG. 6 are exaggerated to facilitate understanding. Here, a description of the deceleration means (impingement on a wall surface) and the third flow rectification means (positioning the valve port at a downstream stagnation point) will be omitted to avoid redundancy.

[0085] As described above, the motor-operated valve 100d in the second joint pipe modification of the second embodiment, like the second embodiment, employs a deceleration means (impact on the wall surface) to eliminate the conventional problem (noise from the motor-operated valve), that is, to suppress the sound of fluid passing through and improve quietness. Furthermore, even if a high-speed foreign object flows into the motor-operated valve 100d from another fluid-connected device, the speed of the foreign object itself can be forcibly decelerated, thereby suppressing damage to the seal portion 20Baa, the valve port 11Ba, etc.

[0086] In addition, the electric valve 100d in the second joint pipe variant of the second embodiment, like the second embodiment, employs a third straightening means (positioning the valve port at the downstream stagnation point), thereby eliminating the concern (uneven flow velocity distribution), further suppressing the sound of fluid passing through the valve port 11Ba, and further improving quietness.

[0087] (Modification of the first joint pipe of the second embodiment) A modified first coupling pipe of the second embodiment will be described with reference to Figure 7. The connection mode of the first coupling pipe 1B' in the modified first coupling pipe of the second embodiment differs from that of the second embodiment in that the first coupling pipe 1B' extending in the direction of the axis L is disposed relative to the valve body 10B'', and the guide member 11B' has a flange one end surface 11Bh (wall surface portion) that directly faces the first port 1Ba'. However, the other configurations are the same as those of the second embodiment. Here, the same configurations are denoted by the same reference numerals, and duplicated explanations will be omitted.

[0088] Specifically, a first joint pipe 1B' extending in the direction of the axis L is connected to the bottom side of the bowl-shaped member 10Ba''. In this way, by arranging the first joint pipe 1B' in the motor-operated valve 100e so that it extends in the direction of the axis L, it is possible to reduce the installation area of ​​the motor-operated valve 100e as viewed in the direction of the axis L.

[0089] <About deceleration methods> The motor-operated valve 100e in the first joint pipe modification of the second embodiment employs a deceleration means (impingement on a wall surface) in the same manner as the first embodiment (see FIG. 2(a)) to suppress fluid passing noise in the valve port 11Ba. This causes the fluid passing through the valve port 11Ba to enter a decelerated flow state, thereby suppressing fluid passing noise and improving quietness. The deceleration means (impingement on a wall surface) in the first joint pipe modification of the second embodiment will be described below. Note that the fluid path (solid line) and the collision portion Ip in FIG. 7 are exaggerated to facilitate understanding of the description.

[0090] <About deceleration methods (collision with wall surface)> The deceleration means (impinging on the wall surface) in the first joint pipe modification of the second embodiment will be described. In the valve open state, as shown by the solid arrow, the fluid flows from the first port 1Ba' through the flow path chamber 13, the valve port 11Ba, the flow path portion 15B, and the internal flow path 14 in this order to the second port 2Ba. Here, the deceleration means (impinging on the wall surface) causes the high-speed fluid flowing from the first port 1Ba' into the flow path chamber 13 to collide with the flange one end face 11Bh (wall surface) directly opposite the first port 1Ba', forcibly slowing down the fluid. As a result, the fluid passing through the valve port 11Ba is in a decelerated flow state, which solves the conventional problem (noise from the motor-operated valve), i.e., suppresses the sound of the fluid passing through and improves quietness.

[0091] <Regarding rectification means> At the collision point Ip where the fluid collides, the high-speed fluid is forcibly decelerated, while multiple three-dimensional vortices are generated around the collision point Ip. If these three-dimensional vortices have a locally high flow velocity and flow directly into the valve port 11Ba without being attenuated, there is a risk of a concern (uneven flow velocity distribution). For this reason, in the first coupling pipe modification of the second embodiment, by further employing a first rectifying means (long fluid path) as in the first embodiment (see FIG. 2(a)), the concern (uneven flow velocity distribution) can be resolved, the fluid passing noise can be further suppressed, and quietness can be further improved.

[0092] <Regarding the first flow straightening means (long fluid path)> 7, the first rectification means (long fluid path) is to lengthen the fluid path from the collision part Ip to the valve port 11Ba, and the viscous resistance of the fluid in this long fluid path can attenuate the generated three-dimensional vortices and make the flow velocity distribution uniform. Specifically, when viewed from the direction of the axis L, the valve port 11a is located on the opposite side of the axis L from the first port 1Ba'. Therefore, the fluid flows from the collision part Ip along the guide member outer peripheral wall 11Bf for at least half a circumference before flowing to the valve port 11Ba.

[0093] As described above, the motor-operated valve 100e in the first coupling pipe modification of the second embodiment employs a deceleration means (impingement on a wall surface), and similarly to the first embodiment, the high-speed fluid flowing from the first port 1Ba' into the flow path chamber 13 is forcibly decelerated by impinging on the flange one end face 11Bh (wall surface) directly opposite the first port 1Ba', thereby eliminating the conventional problem (noise from the motor-operated valve), that is, suppressing the sound of the fluid passing through and improving quietness. Furthermore, even if a high-speed foreign object flows into the motor-operated valve 100e from another fluid-connected device, the speed of the foreign object itself can be forcibly decelerated, thereby suppressing damage to the seal portion (not shown), the valve port 11Ba, etc.

[0094] In addition, the motor-operated valve 100e in the first joint pipe modification of the second embodiment employs a first rectifying means (a long fluid path). As a result, in the first joint pipe modification of the second embodiment, as in the first embodiment, the fluid path from the collision portion Ip to the valve port 11Ba is lengthened, and the multiple three-dimensional vortices generated around the collision portion Ip are attenuated by the viscous resistance of the fluid, thereby making it possible to uniformize the flow velocity distribution. As a result, the motor-operated valve 100e in the first joint pipe modification of the second embodiment resolves the concern (uneven flow velocity distribution), further suppresses the fluid passing noise at the valve port 11Ba, and further improves quietness.

[0095] <About the refrigeration cycle system> A refrigeration cycle system (for cooling operation only) of the present invention will be described using Figure 8. The refrigeration cycle system includes an expansion valve 100 using the motor-operated valves 100a to 100e of the first and second embodiments, an outdoor heat exchanger 200 mounted in an outdoor unit, an indoor heat exchanger 300 mounted in an indoor unit, and a compressor 500. The expansion valve 100, the outdoor heat exchanger 200, the indoor heat exchanger 300, and the compressor 500 are connected to each other by conduits to form a heat pump type refrigeration cycle. Note that an accumulator, a pressure sensor, a temperature sensor, etc. are not shown in the figure.

[0096] During cooling operation (see the solid arrow in the figure), the refrigerant compressed by the compressor 500 is circulated in the order of the outdoor heat exchanger 200, the expansion valve 100, the indoor heat exchanger 300, and the compressor 500, with the outdoor heat exchanger 200 functioning as a condenser and the indoor heat exchanger 300 functioning as an evaporator. Thus, the expansion valve 100 decompresses and expands the liquid refrigerant flowing in from the outdoor heat exchanger 200, and can further control the flow rate of the refrigerant.

[0097] The present invention is not limited to the first and second embodiments, but includes other configurations that can achieve the object of the present invention, and the following modifications are also included in the present invention. For example, the first and second embodiments illustrate motor-operated valves 100a to 100e used in air conditioners such as home air conditioners, but the motor-operated valves of the present invention are not limited to home air conditioners, but may also be used in commercial air conditioners, and are not limited to air conditioners, but can also be applied to various types of refrigerators, etc.

[0098] <Other> It goes without saying that the motor-operated valves 100a to 100e of the present embodiment are applicable not only to the refrigeration cycle illustrated as an example, but also to any other fluid device and fluid circuit. Furthermore, the present invention is not limited to the above-described aspects, embodiments, and modified examples, and can be appropriately changed or modified within the scope of the technical concept of the present invention. [Explanation of symbols]

[0099] 100a, 100b, 100c, 100d, 100e Electric valve 1,1',1B,1B' First joint pipe 1a, 1a', 1Ba, 1Ba' 1st port 2,2B,2B' Second joint pipe 2a, 2Ba, 2Ba' 2nd port 10A, 10B, 10B', 10B'' Valve body 10, 10', 10Ba, 10Ba', 10Ba'' Bowl-shaped member 10a ridge 11, 11B, 11B' Guide member 11a, 11Ba valve port 11b,11Bb Valve seat 11d Guide section 11e,11Be Support part 11Bca Small diameter guide part (guide part) 11Bcb Large diameter guide part (guide part) 11Bf Guide member outer wall (wall surface) 11Bg Drawer section 11Bh One end of the flange (wall) 12 Lower lid 13 Flow path chamber 14 Internal flow path 15, 15B Flow path section 15a One end 15b Other end 16 Containment Space 17 Retaining ring 18 Connecting Room 20A, 20B Valve body 20a,20Ba valve part 20aa, 20Baa seal part 20ab Valve part outer peripheral wall (wall part) 20b One end side bottomed cylindrical part 20ba other end 20c,20Bc Other end side bottomed cylindrical part 20d stepped section 20e protrusion 20f Annular groove 20g flange 20ga flange end (wall) 20Bg small diameter guide shaft 20Bh Large diameter guide shaft 20Bi One end stepped part 20Bk disc part 20Bka Other end stepped section 20Bkb protrusion 30A, 30B stepping motor 31,31B Case 32,32B magnet rotor 33, 33B Stator coil 34, 34B Magnet part 35,35B hub 40A, 40B Support member 41 Spring holder 42 biasing spring 43 Bush 100 Expansion valve 200 Outdoor heat exchanger 300 Indoor heat exchanger 400 Flow path switching valve 500 compressor Ip collision part L axis

Claims

1. a valve body having a valve portion provided on one end side thereof, and a rotor portion having a rotor that rotates integrally with the valve body; a valve body including a flow path chamber that accommodates the valve portion, a valve seat that faces the valve portion in a radial direction, and a valve port that extends in a radial direction and is capable of communicating with the flow path chamber; a case connected to the valve body and defining an accommodation space for the rotor portion; a deceleration means for decelerating the velocity of fluid passing through said valve port; Equipped with the valve body includes a bowl-shaped member that defines a portion of the flow path chamber, a guide portion that is integrally formed with the bowl-shaped member and that supports the valve element, which is provided along an axis, in the axial direction and guides it in the circumferential direction, a first port that directly communicates with the flow path chamber, and a second port that communicates with the valve port, the valve portion has a seal portion that closes the valve port and a flow path portion that can communicate with the valve port, the rotation of the rotor changes the state of communication between the valve port and the flow path portion, thereby controlling the flow rate of the fluid flowing through the valve port; The motor-operated valve, wherein the deceleration means is such that the valve body or the guide portion has a wall portion directly facing the first port.

2. The guide portion is made of a guide member formed in a bottomed cylindrical shape having a bottom portion on the other end side, 2. The motor-operated valve according to claim 1, wherein the valve body and the outer peripheral surface of the guide portion have sliding portions that are slidably engaged with each other.

3. 2. The motor-operated valve according to claim 1, wherein the valve body and the inner circumferential surface of the guide portion have sliding portions that are slidably engaged with each other.

4. a flow rectifying means for uniformly distributing a flow velocity of the fluid passing through the valve port; 2. The motor-operated valve according to claim 1, wherein the flow rectifying means arranges the valve port on the opposite side of the axis from the first port when viewed in the axial direction.

5. a flow rectifying means for uniformly distributing a flow velocity of the fluid passing through the valve port; 3. The motor-operated valve according to claim 2, wherein the flow path portion of the flow straightening means extends along the axial direction and has a flow path area substantially equal to the flow path area of ​​the valve port.

6. a flow rectifying means for uniformly distributing a flow velocity of the fluid passing through the valve port; 4. The motor-operated valve according to claim 3, wherein the flow rectifying means is arranged in the guide portion such that the valve port is located on the opposite side of the wall portion with respect to the axis when viewed in the axial direction.

7. A refrigeration cycle system including a compressor, a condenser, an expansion valve, and an evaporator, wherein the motor-operated valve according to any one of claims 1 to 6 is used as the expansion valve.

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